US20140260392A1 - Apparatus and methods for heating water with refrigerant from air conditioning system - Google Patents
Apparatus and methods for heating water with refrigerant from air conditioning system Download PDFInfo
- Publication number
- US20140260392A1 US20140260392A1 US14/210,383 US201414210383A US2014260392A1 US 20140260392 A1 US20140260392 A1 US 20140260392A1 US 201414210383 A US201414210383 A US 201414210383A US 2014260392 A1 US2014260392 A1 US 2014260392A1
- Authority
- US
- United States
- Prior art keywords
- refrigerant
- air
- control system
- heat exchanger
- path
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 239000003507 refrigerant Substances 0.000 title claims abstract description 443
- 238000004378 air conditioning Methods 0.000 title claims abstract description 134
- 239000008236 heating water Substances 0.000 title claims abstract description 17
- 238000000034 method Methods 0.000 title description 15
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 438
- 239000003570 air Substances 0.000 claims description 251
- 230000001143 conditioned effect Effects 0.000 claims description 88
- 238000004891 communication Methods 0.000 claims description 76
- 238000012546 transfer Methods 0.000 claims description 27
- 230000004044 response Effects 0.000 claims description 18
- 239000012530 fluid Substances 0.000 claims description 8
- 239000012080 ambient air Substances 0.000 claims description 5
- 238000010438 heat treatment Methods 0.000 abstract description 108
- 238000001816 cooling Methods 0.000 description 60
- 239000007788 liquid Substances 0.000 description 19
- 230000006870 function Effects 0.000 description 18
- 239000007789 gas Substances 0.000 description 17
- 230000008859 change Effects 0.000 description 14
- 238000010586 diagram Methods 0.000 description 12
- 239000012071 phase Substances 0.000 description 10
- 230000009467 reduction Effects 0.000 description 9
- 230000008569 process Effects 0.000 description 8
- 230000004913 activation Effects 0.000 description 7
- 230000003750 conditioning effect Effects 0.000 description 7
- 230000007704 transition Effects 0.000 description 7
- 230000000694 effects Effects 0.000 description 5
- 238000012545 processing Methods 0.000 description 5
- 230000002441 reversible effect Effects 0.000 description 5
- 230000003213 activating effect Effects 0.000 description 4
- 230000007423 decrease Effects 0.000 description 4
- 230000009977 dual effect Effects 0.000 description 4
- 230000004048 modification Effects 0.000 description 4
- 238000012986 modification Methods 0.000 description 4
- 230000008901 benefit Effects 0.000 description 3
- 239000002184 metal Substances 0.000 description 3
- 229910052751 metal Inorganic materials 0.000 description 3
- 230000000153 supplemental effect Effects 0.000 description 3
- 238000012360 testing method Methods 0.000 description 3
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 2
- 230000009471 action Effects 0.000 description 2
- 229910052802 copper Inorganic materials 0.000 description 2
- 239000010949 copper Substances 0.000 description 2
- 230000009849 deactivation Effects 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 239000007791 liquid phase Substances 0.000 description 2
- 230000003134 recirculating effect Effects 0.000 description 2
- 230000006903 response to temperature Effects 0.000 description 2
- 238000013459 approach Methods 0.000 description 1
- 230000000052 comparative effect Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 239000007792 gaseous phase Substances 0.000 description 1
- 230000000977 initiatory effect Effects 0.000 description 1
- 238000009413 insulation Methods 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 239000004973 liquid crystal related substance Substances 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 230000005055 memory storage Effects 0.000 description 1
- 230000002085 persistent effect Effects 0.000 description 1
- 238000012797 qualification Methods 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H4/00—Fluid heaters characterised by the use of heat pumps
- F24H4/02—Water heaters
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D15/00—Other domestic- or space-heating systems
- F24D15/04—Other domestic- or space-heating systems using heat pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D17/00—Domestic hot-water supply systems
- F24D17/0005—Domestic hot-water supply systems using recuperation of waste heat
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D17/00—Domestic hot-water supply systems
- F24D17/0026—Domestic hot-water supply systems with conventional heating means
- F24D17/0031—Domestic hot-water supply systems with conventional heating means with accumulation of the heated water
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D17/00—Domestic hot-water supply systems
- F24D17/02—Domestic hot-water supply systems using heat pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D19/00—Details
- F24D19/10—Arrangement or mounting of control or safety devices
- F24D19/1006—Arrangement or mounting of control or safety devices for water heating systems
- F24D19/1051—Arrangement or mounting of control or safety devices for water heating systems for domestic hot water
- F24D19/1054—Arrangement or mounting of control or safety devices for water heating systems for domestic hot water the system uses a heat pump
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
- F24F5/0096—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater combined with domestic apparatus
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H15/00—Control of fluid heaters
- F24H15/20—Control of fluid heaters characterised by control inputs
- F24H15/212—Temperature of the water
- F24H15/223—Temperature of the water in the water storage tank
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H15/00—Control of fluid heaters
- F24H15/20—Control of fluid heaters characterised by control inputs
- F24H15/254—Room temperature
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H15/00—Control of fluid heaters
- F24H15/30—Control of fluid heaters characterised by control outputs; characterised by the components to be controlled
- F24H15/355—Control of heat-generating means in heaters
- F24H15/36—Control of heat-generating means in heaters of burners
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H15/00—Control of fluid heaters
- F24H15/30—Control of fluid heaters characterised by control outputs; characterised by the components to be controlled
- F24H15/355—Control of heat-generating means in heaters
- F24H15/37—Control of heat-generating means in heaters of electric heaters
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H15/00—Control of fluid heaters
- F24H15/30—Control of fluid heaters characterised by control outputs; characterised by the components to be controlled
- F24H15/375—Control of heat pumps
- F24H15/39—Control of valves for distributing refrigerant to different evaporators or condensers in heat pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H4/00—Fluid heaters characterised by the use of heat pumps
- F24H4/02—Water heaters
- F24H4/04—Storage heaters
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H6/00—Combined water and air heaters
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
- F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
- F25B49/027—Condenser control arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
- F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/06—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with the heat-exchange conduits forming part of, or being attached to, the tank containing the body of fluid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D2200/00—Heat sources or energy sources
- F24D2200/04—Gas or oil fired boiler
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D2200/00—Heat sources or energy sources
- F24D2200/08—Electric heater
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D2200/00—Heat sources or energy sources
- F24D2200/12—Heat pump
- F24D2200/123—Compression type heat pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D2200/00—Heat sources or energy sources
- F24D2200/16—Waste heat
- F24D2200/24—Refrigeration
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2221/00—Details or features not otherwise provided for
- F24F2221/18—Details or features not otherwise provided for combined with domestic apparatus
- F24F2221/183—Details or features not otherwise provided for combined with domestic apparatus combined with a hot-water boiler
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H15/00—Control of fluid heaters
- F24H15/20—Control of fluid heaters characterised by control inputs
- F24H15/227—Temperature of the refrigerant in heat pump cycles
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H15/00—Control of fluid heaters
- F24H15/40—Control of fluid heaters characterised by the type of controllers
- F24H15/414—Control of fluid heaters characterised by the type of controllers using electronic processing, e.g. computer-based
- F24H15/45—Control of fluid heaters characterised by the type of controllers using electronic processing, e.g. computer-based remotely accessible
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of condensers
- F25B2339/047—Water-cooled condensers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/04—Refrigeration circuit bypassing means
- F25B2400/0403—Refrigeration circuit bypassing means for the condenser
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2501—Bypass valves
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B10/00—Integration of renewable energy sources in buildings
- Y02B10/70—Hybrid systems, e.g. uninterruptible or back-up power supplies integrating renewable energies
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/12—Hot water central heating systems using heat pumps
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/52—Heat recovery pumps, i.e. heat pump based systems or units able to transfer the thermal energy from one area of the premises or part of the facilities to a different one, improving the overall efficiency
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
Definitions
- An embodiment of an apparatus for heating water includes a tank for storing water, and a heater exchanger in thermal communication with the tank and configured to receive refrigerant and transfer heat therefrom to the tank.
- An air conditioning system has an air handler actuatable to move an air flow through an air flow path into a conditioned space.
- a refrigerant path has a first portion that passes through the air flow path and a second portion that passes through the heat exchanger.
- a pump is disposed in the refrigerant path and is actuatable to move refrigerant through the refrigerant path.
- a control system is in operative communication with the air handler to control actuation of the air handler and is in operative communication with the pump to control actuation of the pump.
- control system In a first mode of operation, the control system actuates the air handler to move the air flow through the air flow path and actuates the pump to move refrigerant through the first portion of the refrigerant path and the second portion of the refrigerant path. In a second mode of operation, the control system maintains the air handler in an inactive state and actuates the pump to move refrigerant through the first portion of the refrigerant path and the second portion of the refrigerant path.
- an apparatus for heating water includes a tank for storing water and a temperature sensor in thermal communication with water in the tank and configured to output a first signal corresponding to temperature of the water.
- a heat exchanger is in thermal communication with the tank and is configured to receive refrigerant and transfer heat therefrom to the tank.
- An air conditioning system has an air handler actuatable to move an air flow through an air flow path into a conditioned space.
- a refrigerant path has a first portion that passes through the air flow path and a second portion that passes through the heat exchanger.
- a valve system within the refrigerant path controls refrigerant flow to the first portion and the second portion and is selectively configurable to alternatively allow refrigerant flow through the second portion and block refrigerant flow through the second portion.
- a pump is disposed in the refrigerant path and is actuatable to move refrigerant through the refrigerant path.
- a thermostat is operable to measure ambient temperature in the conditioned space and to output a second signal corresponding to ambient temperature in the conditioned space.
- a control system is in operative communication with the tank to receive the first signal, is in operative communication with the air handler to control actuation of the air handler, is in operative communication with the pump to control actuation of the pump, is in operative communication with the valve system to selectively allow refrigerant flow through the second portion and block refrigerant flow through the second portion, and is in operative communication with the thermostat to receive the second signals.
- the control system in response to the first and second signals, in a first mode of operation, actuates the air handler to move the air flow through the air flow path, actuates the pump to move refrigerant through the refrigerant path, and configures the valve system to allow refrigerant flow through the second portion.
- control system In a second mode of operation, the control system maintains the air handler in an inactive state, actuates the pump to move refrigerant through the refrigerant path, and configures the valve system to allow refrigerant flow through the second portion.
- control system In a third mode of operation, the control system actuates the air handler to move the air flow through the air flow path, actuates the pump to move refrigerant through the refrigerant path, and configures the valve system to block refrigerant flow through the second portion.
- an apparatus for heating water has a tank for storing water and having a heat source.
- a heat exchanger is in thermal communication with the tank and is configured to receive refrigerant and transfer heat therefrom to the tank.
- An air conditioning system has an air handler actuatable to move an air flow through an air flow path into a conditioned space.
- a refrigerant path has a first portion that passes through the air flow path and a second portion that passes through the heat exchanger.
- a pump is disposed in the refrigerant path and is actuatable to move refrigerant through the refrigerant path.
- a plurality of sensors respectively output signals representative of respective system operating parameters.
- a control system is in operative communication with the tank to control operation of the heat source, is in operative communication with the air handler to control actuation of the air handler, is in operative communication with the sensors to receive the respective signals, and is in operative communication with the refrigerant path to control refrigerant flow.
- the control system selectively allows or blocks refrigerant flow through the second portion and selectively actuates the water heater heat source.
- an apparatus for heating water has a tank for storing water and having a heat source.
- a heat exchanger is in thermal communication with the tank and is configured to receive refrigerant and transfer heat therefrom to the tank.
- An air conditioning system has an air handler actuatable to move an air flow through an air flow path into a conditioned space.
- a refrigerant path has a first portion that passes through the air flow path and a second portion that passes through the heat exchanger.
- a pump is disposed in the refrigerant path and is actuatable to move refrigerant through the refrigerant path.
- a valve system within the refrigerant path controls refrigerant flow in the first portion and the second portion and is selectively configurable to alternatively allow refrigerant flow through the second portion and block refrigerant flow through the second portion.
- a plurality of sensors each outputs a respective signal representative of a respective system operating parameter that varies in a predetermined relationship with operating efficiency of at least one of the tank and the air conditioning system.
- a control system is in operative communication with the tank to control operation of the heat source, is in operative communication with the air handler to control actuation of the air handler, is in operative communication with the sensors to receive the respective signals, and is in operative communication with the valve system to control refrigerant flow.
- the control system selectively actuates the valve system to allow refrigerant flow through the second portion or block refrigerant flow through the second portion and selectively actuates the water heater heat source.
- FIG. 1 is a schematic view of an air conditioning system according to an embodiment of the present invention, with an air conditioning system providing only conditioned space air conditioning;
- FIG. 2 is a schematic diagram of the system as in FIG. 1 , but with the air conditioning system providing conditioned space air and providing refrigerant heat to a water heater;
- FIG. 3 is a schematic diagram of the system as in FIG. 2 , but with the air conditioning system providing refrigerant heat to one of two water heater tanks in a two water heater tank arrangement;
- FIG. 4 is a schematic diagram of a an air conditioning system according to an embodiment of the present invention, with an air conditioning system providing only conditioned space air cooling;
- FIG. 5 is a schematic diagram of the system as in FIG. 4 , but with the air conditioning system providing conditioned space air and providing refrigerant heat to a water heater;
- FIG. 6 is a schematic diagram of the system as in FIG. 4 , but with the air conditioning system providing conditioned space air heating without providing refrigerant heat to a water heater;
- FIG. 7 is a schematic diagram of the system as in FIG. 4 , but with the air conditioning system providing conditioned space air and providing refrigerant heat to a water heater;
- FIG. 8 is a schematic diagram of an air conditioning system according to an embodiment of the present invention.
- FIG. 9 is a schematic diagram of the system as in FIG. 8 , but with the air conditioning system providing conditioned space air cooling without providing refrigerant heat to a water heater;
- FIG. 10 is a schematic diagram of the system as in FIG. 8 , but with the air conditioning system providing conditioned space air heating without providing refrigerant heat to a water heater;
- FIG. 11 is a schematic diagram of the system as in FIG. 8 , but with the air conditioning system providing conditioned space air and providing refrigerant heat to a water heater;
- FIG. 12 is a schematic diagram of the system as in FIG. 8 , but with the air conditioning system providing conditioned space air and providing refrigerant heat to a water heater; and
- FIG. 13 is a schematic diagram of the system as in FIG. 8 , but with the air conditioning system providing refrigerant heat to a water heater without providing conditioned space air.
- air conditioning apparatus encompass apparatus useable to change the temperature of air being delivered to a conditioned space and having an associated refrigerant circuit.
- an “air conditioning” apparatus or system may comprise, without limitation, (1) an air conditioning unit (or “air conditioner”) having a non-reversible refrigerant circuit that may be used to cool air delivered to a conditioned space, or (2) a heat pump having a reversible refrigerant circuit that may be used to heat or cool air delivered to a conditioned space.
- air conditioning unit or “air conditioner” having a non-reversible refrigerant circuit that may be used to cool air delivered to a conditioned space
- a heat pump having a reversible refrigerant circuit that may be used to heat or cool air delivered to a conditioned space.
- Residential and commercial air conditioning systems capture heat at some point in the refrigerant's continuous cycle and transfer the heat to a point inside or outside the building, depending upon whether the system is functioning in a cooling mode or, if capable of dual modes, in a heating mode.
- a portion of that heat may be captured and used to heat water in the building's water heater to a temperature at or, more often, below a high set point temperature of the water heater.
- An electric element or gas burner in the water heater may provide additional heat to bring the water temperature up to the water heater's high set point temperature.
- FIGS. 1 and 2 An air conditioning/water heater system 10 embodying principles of an embodiment of the present invention is schematically depicted in FIGS. 1 and 2 and includes (1) an air conditioning system 12 having an outdoor condensing coil unit 14 and an indoor evaporating coil unit 16 , and (2) an associated water heater 18 which, representatively, may be a gas-fired or electric water heater.
- air conditioning system 12 is arranged so that it operates in an air cooling mode only, and in FIG. 2 is in an air cooling mode and further provides supplemental, refrigerant-based heat to water heater 18 .
- the various functions of air conditioning/water heater system 10 are controlled by a schematically depicted electronic control circuit 20 (shown only in FIG. 1 ) that operates various subsequently described components of the overall system 10 .
- an air conditioning system from the standpoint of refrigerant flow, comprises a closed loop of refrigerant flowing among a compressor (i.e. a pump), a condenser coil, and an evaporator coil.
- a compressor i.e. a pump
- condenser coil i.e. a condenser coil
- evaporator coil i.e. a condenser coil
- one of the two coils is disposed inside the enclosure that is receiving conditioned air (the conditioned space, e.g. a building interior space), in association with an air handler, while the other coil is disposed outside the enclosure of the conditioned space, in the ambient environment.
- the compressor may be inside or outside the enclosure, such as a building interior, but is typically outside in a housing that also encloses the outside coil.
- the outdoor coil is the condenser
- the indoor coil is an evaporator.
- Refrigerant flows from the compressor, to the outdoor condenser coil, to the indoor evaporator coil, and back to the compressor.
- the outdoor unit includes a fan that draws ambient air across the condenser coils to draw heat from the coils.
- the refrigerant acquires this heat in part from the indoor air at the evaporator as the liquid refrigerant evaporates in the coil in response to the influence of an expansion valve at the coil's input.
- the refrigerant removes energy (i.e. heat) from the indoor air, thereby cooling the air as it is forced back into the building's conditioned space.
- the warm refrigerant gas then flows from the evaporator coil to the compressor, which receives the gas and pumps it back to the condenser, adding pressure and heat.
- refrigerant lines between the compressor and the condenser, and between the compressor and the evaporator pass through a reversing valve so that, when switching from cooling mode to a heating mode, the control system actuates the reversing valve to direct the compressor output to the indoor coil, rather than to the outdoor coil.
- the roles of the indoor and outdoor coils reverse from those the coils have in air cooling modes, but the sequence of compressor-condenser-evaporator-compressor remains.
- the condenser cools the refrigerant, thereby dissipating the refrigerant's acquired heat (from the evaporator and the compressor) to the ambient environment via the air flow that the fan moves over the coil.
- the temperature reduction in the condenser also reduces the refrigerant's volume, in turn reducing its pressure, but the refrigerant flow path length and tubing dimensions, and the compressor's size and strength, are selected so that sufficient positive and negative pressure remain at the condenser's output and input to continue refrigerant flow to the evaporator and therefrom back to the compressor.
- the selection of such system components and operating parameters to enable desired heat transfer and recirculating refrigerant flow through the flow circuit should be well understood in this art. While it should be understood that the air conditioning systems described below are designed to provide sufficient heat transfer and pressure to maintain system operation, these variables are not discussed further herein.
- One or more embodiments of the present invention described herein insert into the refrigerant path a cooling coil that is proximate a water heater to be in thermal communication with the water heater tank and thereby transfer heat from the flowing refrigerant to water in the tank.
- the addition of the cooling coil does not disrupt the air conditioning system's underlying compressor-condenser-evaporator-compressor sequence, but it is nonetheless encompassed within the present disclosure to use a single coil, wrapped around a water heater tank and functioning as both the heat exchanger and the air conditioning system condenser, in conditions where the heat exchanger provides sufficient cooling for the air conditioning system's condenser needs and where the air conditioning system does not require air flow over the condenser.
- the present disclosure primarily discusses examples having a fan-driven system condenser and a distinct water heater heat transfer coil, it should be understood that other arrangements fall within the present disclosure.
- Control system 20 may comprise a programmable logic controller (PLC) that operates as the general system controller. Housed, for example, with outdoor unit 14 , the PLC communicates with and controls (via suitable electrical connections, relays, power sources, and other electromechanical connections, as should be understood in this art) the actuation and operation of the components described herein, including but not limited to the compressor, outdoor coil fan, indoor coil fan, and all electrically controlled valves. As such, the control system communicates with and controls the air conditioning system, including the valve system within the refrigerant flow path that, in conjunction with the compressor (also controlled by the control system) controls refrigerant flow.
- PLC programmable logic controller
- connection between control system 20 and each of outdoor unit 14 , indoor unit 16 , and water heater 18 encompass such communications and control.
- Such communication may also encompass communication between the control system and a temperature sensor at the outdoor unit, which provides a signal to the control system corresponding to temperatures of the outdoor unit's ambient environment.
- control system 20 receives input signals from one or more thermostats in the building's conditioned space that provide instructions regarding whether to activate the air conditioning system, deactivate the air conditioning system, actuate the air handler fan, operate the system in air cooling mode, and (where the air conditioning system is a heat pump) operate the system in air heating mode.
- the thermostat being located in the conditioned space and including a temperature sensor, may also output to the control system a signal corresponding to temperature of the conditioned space.
- the operation of thermostats in generating such instructions should be well understood and is, therefore, not discussed further herein.
- the thermostat may be considered a part of control system 20 , and, in any event, functions typically performed by the thermostat can be shared or performed by control system 20 .
- controller 20 and indoor unit 16 encompass such communications between the control system and the thermostat(s), as well as communication between the control system and the air handler and between the control system and the water heater.
- the control system activates and deactivates the air handler, based on the air conditioning system programming in response to signals from the thermostat and possibly signals from sensors indicating system operating parameters, as should be understood. In an inactive state, the air handler does not force air into, draw air into, or otherwise move air through the conditioned space.
- actuation of the air conditioning system may refer to activation of the compressor to move refrigerant through the refrigerant path, activation of the condenser fan, and activation of the air handler (fan), in certain embodiments. But as discussed herein, in some circumstances the air conditioning system may be actuated without activating the air handler. In that sense, the control system activates the air conditioning system while maintaining the air handler in an inactive state.
- Reference to communication between controller 20 / 50 / 120 and indoor unit 16 / 66 / 116 also encompasses communication between the control system and the water heater, e.g. the water heater controller or, particularly where the water heater controller's functions are incorporated by the control system, between the control system and the water heater temperature sensor(s) and heat source(s).
- water heater 18 may include an electronic controller (not shown) that can receive manual or electronic instructions to activate and deactivate a water heater and can respond to such instructions as well as activating and deactivating the water heater in response to pre-programmed set point temperatures.
- the water heater's high and low set point temperatures are typically capable of manual or electronic setting by the operator and/or at installation.
- the water heater's controller monitors the output of one or more temperature sensors in thermal communication with water inside the water heater and compares the water temperature with the predetermined set points. If the water heater is in an inactive state, and if the water tank temperature is above the water heater's low set point, the water heater controller takes no action until the water tank temperature reaches or falls below the low set point. At this point, the water heater controller activates the water heater's internal heat source, which begins to heat the water. The water heater controller continues to receive and monitor water temperature signals from the one or more water heater temperature sensors, and maintains the water heater heat source active until the controller receives a signal from the one or more temperature sensors indicating that the water heater temperature has exceeded the high set point. The water heater goes back to an inactive mode and does not reactivate until manually activated or until the signal from the one or more temperature sensors indicates that the water temperature has again fallen to or below the low set point.
- the water heater controller passes the water heater temperature sensor signals or corresponding data to control system 20 / 70 / 120 , which then determines whether to heat the water heater with refrigerant heat or with the water heater's inherent heat source, as described above. If, or when, the control system decides to operate the water heater heat source, the control system sends a corresponding signal to the water heater controller, which actuates the heat source. The water heater controller may thereafter monitor water temperature and deactivate the heat source when the temperature reaches the high set point, or it may continue to pass the temperature signal or data to the control system, which makes the decision when to deactivate the water heater heat source and sends an appropriate instruction signal to the water heater controller.
- the water heater controller may be omitted, and the control system 20 / 70 / 120 put in direct communication with the water heater temperature sensor(s) and heat source control (i.e. activation and deactivation control) in order to perform the functions described herein.
- control systems 20 and 70 communicate with variable fan controllers 25 and 115 , and the communications indicated between control systems 20 and 70 and outdoor and indoor units 14 / 64 and 16 / 66 reflect such communications. Still further, however, the functions of the variable fan controllers may also be incorporated entirely within the control system, so that the fan controllers may be omitted and the control system communicates directly with temperature sensors 27 / 117 , or 42 or 46 .
- control system 20 / 70 / 120 may be embodied by computer-executable instructions of a program that executes on one or more computers, for example embodied by a residential or commercial split system air conditioning system controller.
- program modules include routines, programs, components, data structures, etc., that perform particular tasks and/or implement particular abstract data types.
- systems/methods described herein may be practiced with various controller configurations, including programmable logic controllers, simple logic circuits, single-processor or multi-processor systems, as well as personal computers, hand-held computing devices, microprocessor-based or programmable consumer or industrial electronics, and the like.
- control system 20 may comprise a computing device that communicates with the system components described herein via hard wire or wireless local or remote networks.
- a controller that could effect the functions described herein could include a processing unit, a system memory and a system bus.
- the system bus couples the system components including, but not limited to, system memory to the processing unit.
- the processing unit can be any of various available programmable devices, including microprocessors, and it is to be appreciated that dual microprocessors, multi-core and other multi processor architectures can be employed as the processing unit.
- Software applications may act as an intermediary between users and/or other computers and the basic computer resources of electronic control system 20 , as described, in suitable operating environments. Such software applications include one or both of system and application software.
- System software can include an operating system that acts to control and allocate resources of control system 20 .
- Application software takes advantage of the management of resources by system software through the program models and data stored on system memory.
- the controller may also, but does not necessarily, include one or more interface components that are communicatively coupled through the bus and facilitate interaction with the control system.
- the interface component can be a port (e.g., serial, parallel, PCMCIA, USC, or FireWire) or an interface card, or the like.
- the interface component can receive input and provide output (wired or wirelessly). For instance input can be received from devices including but not limited to a pointing device such as a mouse, track ball, stylus, touch pad, key pad, touch screen display, keyboard, microphone, joy stick, gamepad, satellite dish, scanner, camera, or other component.
- Output can also be supplied by control system 20 to output devices via the interface component.
- Output devices can include displays (for example cathode ray tubes, liquid crystal display, light emitting diodes, or plasma) whether touch screen or otherwise, speakers, printers, and other components.
- control system 20 received inputs from, and directs outputs to, the various components with which control system 20 communicates, as described herein.
- the control system receives signals from the thermostat, the water heater, and possibly temperature sensors or other operating parameter sensors that are not part of the thermostat or water heater.
- the controller activates or deactivates the air conditioning system to provide or stop the provision of conditioned air to a conditioned space in response to the thermostat signals. It decides whether to activate a water heating source in response to the water heating signal, and it decides which water heating heat source to utilize in response to the water heater signals and the operating parameter signals (which may include the thermostat signal) and in some instances in response to the air conditioning mode in which the air conditioning system exists.
- the apparatus for carrying out these functions, and the manner of their operation, are described below.
- outdoor condensing unit 14 includes a condenser coil 22 , an associated condenser fan 24 , and a compressor 26 .
- the condenser coil and compressor are coupled, as shown, by a refrigerant tubing circuit 28 and liquid refrigerant line portions 30 and 32 , to indoor unit evaporator coil 34 and to a heat conductive refrigeration tube spiral-wrapped around a metal tank portion 36 of water heater 18 and serving as a refrigerant to tank water heater exchanger 38 for water heater 18 .
- a single coil is illustrated, multiple parallel coils may be utilized to reduce pressure drop through the heat exchanger.
- reference to a heat exchanger “coil” encompasses one or multiple coils, in series or in parallel. It will also be understood that the coils may be covered in insulation.
- an electronically controlled regulator valve 40 with an associated refrigerant temperature sensor 42 installed as shown in refrigerant tubing circuit 28 within condensing unit 14 (2) an electronically controlled regulator valve 44 and an associated refrigerant temperature sensor 46 installed as shown in refrigerant tubing circuit 28 between line 32 and (adjacent to) a refrigerant inlet 48 of heat exchanger coil 38 , and (3) a normally open solenoid valve 50 installed in a refrigerant bypass line 32 a between heat exchanger inlet 48 and a heat exchanger refrigerant outlet 52 .
- water to be heated flows into water heater tank 36 via a water inlet pipe 54 and, in response to a heated water demand, is discharged from tank 36 via a hot water supply pipe 56 .
- FIGS. 1-7 illustrate temperature sensors 42 , 46 , 27 , 102 , and 117 .
- temperature sensors 27 and 117 are utilized by fan controllers 25 and 115 , respectively, in variably driving the outdoor and indoor coil fans.
- Each of temperature sensors 42 , 46 , and 102 illustrate other positions at which temperature sensors may be placed to provide temperature information to drive control of the outdoor fan, in place of temperature sensor 27 .
- These sensors should, therefore, be understood as alternatives to sensor 27 and may be omitted in the presence of sensor 27 .
- valves As will be understood, the normally open or normally closed valves transition between open or closed states, whereas the proportional valves can be used to meter fluid flow if desired. In the examples discussed herein, all the electronically controlled valves transition between fully open and fully closed states, and it is thus encompassed within the present disclosure that all valves may be non-proportional valves. It should also be understood, however, that the use of proportional valves to meter fluid flow, for example via the condenser bypass valves, is encompassed within the scope of the present disclosure.
- An expansion valve 58 is disposed in line 32 at an inlet to indoor coil 34 .
- an expansion valve receives a fluid input at a high pressure and, depending on the settings within the valve, outputs the fluid at a lower pressure. This allows pressurized refrigerant entering coil 34 (when used as an evaporator) to drop in pressure in the evaporator coil and change phase from a liquid to a gas.
- control system 20 receives a signal from controller or a temperature sensor in water heater 18 indicating that the tank's water temperature is above the water heater's low set point, which is stored in the control system's memory. That is, no water heating is called for. Assume, also, that control system 20 has received a signal from the building's thermostat (not shown) requiring the air conditioning system to provide cool air to the conditioned space. With air conditioning system 12 accordingly in an air cooling-only mode, without need for the control system to also select and actuate a water heating heat source (e.g.
- gaseous refrigerant flows from evaporator coil 34 to compressor 26 via suction line 30 .
- Compressor 26 pumps the gaseous refrigerant forward, increasing the refrigerant's pressure and temperature and causing the now-hotter refrigerant gas to flow through condenser coil 22 .
- Control system 20 actuates fan 24 (at a constant speed) via a variable fan speed control 25 to thereby push or draw air over the condenser coils, causing the gaseous refrigerant to cool in coil 22 and thereby change phase from a gas to a liquid.
- control system 20 maintains valve 40 , between the condenser and the compressor, closed. Since no water heating is called for, control system 20 maintains valve 44 closed and valve 50 in its normally fully open position.
- control system 20 controls the operation of heat exchanger 38 in response to receipt of temperature information from a water heater controller or from a temperature sensor at tank 36 .
- water heater 18 typically operates between low and high temperature set points.
- control system 20 rather than the water heater's independent control, responds to water heater water temperature when it falls below the water heater's low set point, selecting between the water heater's inherent heat source and heat exchanger 38 as the means by which to add heat to the water heater, depending upon which heat source results in higher overall system efficiency. The basis for this decision is discussed in more detail below.
- control system 20 when water heater 18 requires refrigerant heat (as determined by comparison of the value of a temperature signal from the non-illustrated temperature sensor in a bottom portion of tank 36 to the stored water tank low set point), control system 20 ( FIG. 1 ) appropriately positions the various previously described valves 40 , 44 , and 50 to which it is linked to cause the refrigerant traversing tubing circuit 28 from the outdoor unit to pass through heat exchanger 38 , thereby adding refrigerant heat to water in tank 36 , before flowing to evaporator coil 34 .
- control system 20 When control system 20 detects that heating responsibility should shift from the heat exchanger to the water heater heat source, or that water heater 18 no longer needs refrigerant heat, as described below, it returns air conditioning system 12 to its air cooling-only mode, as discussed with regard to FIG. 1 , in which all of the refrigerant flow traversing tubing circuit 28 bypasses water heater coiled tube heat exchanger 38 .
- control system 20 switches fan speed controller 25 from full speed (at which fan 24 is operated during air cooling-only mode) to a variable speed mode (in which fan speed controller 25 controls the speed of fan 24 in response to a temperature sensor 27 , as described below), opens valve 44 , closes valve 50 , and opens valve 40 .
- the control system directs the entirety of the refrigerant flow through heat exchanger 38 .
- the condenser coil receives only part of the refrigerant flow output from compressor 26 .
- the refrigerant flowing from condenser 22 and valve 40 to heat exchanger 28 contains both cooler liquid and warmer gaseous refrigerant. That is, the refrigerant flow includes hot gaseous refrigerant that, but for bypass valve 40 , would have cooled and condensed in coil 22 but is instead diverted to coil 38 , which in turn cools the refrigerant, condenses the gaseous refrigerant component of the dual phase refrigerant flow that reaches the heat exchanger, and transfers the removed heat to water within water heater tank 36 . Accordingly, heat exchanger 38 may be considered a sub-condenser or sub-cooler of the overall condenser, as it completes the condensing function begun by condenser coil 22 .
- Valve 40 therefore, effectively diverts heat from the compressor output to the heat exchanger that the condenser would otherwise have removed.
- the amount of heat that the valve diverts is defined by the balance of refrigerant flow between valve 40 and coil 22 . This balance is, in turn, defined by the speed of fan 24 .
- the bypass refrigerant flowing through valve 40 is warmer than the condensed refrigerant flowing through condenser coil 22 .
- the cooler, condensed refrigerant presents less resistance to flow through the condenser coil than does the hot gaseous refrigerant through bypass valve 40 , even though the bypass valve path is much shorter in length.
- variable fan controller 25 reduces the speed of fan 24 when water heating is needed. This reduces the rate at which air flows over the condenser coils, thereby reducing the rate at which refrigerant in the condenser coil cools and correspondingly increasing the resistance to refrigerant flow. This, in turn, increases refrigerant flow through the bypass valve and increases the heat contributed to the heat exchanger.
- control system 50 downloads a target temperature to fan controller 25 .
- controller 25 receives a signal from controller 20 indicating that water heating mode has begun, fan controller 25 ceases full speed fan operation and compares the output of temperature sensor 27 to the target temperature. If the sensor 27 temperature is above the target temperature, controller 25 increases the speed of fan 24 , which thereby draws air over (and cools) the refrigerant in the coil at a higher rate, and reduces the amount of hot bypass refrigerant flowing through valve 40 .
- controller 25 decreases the speed of fan 24 , thereby reducing the heat removed from the refrigerant, and increasing its flow resistance, to thereby allow more hot gaseous refrigerant to bypass the condenser coil.
- the target temperature represents the temperature at which the condenser/bypass combination provides refrigerant to the heat exchanger.
- the target temperature preferably does not exceed the temperature at which compressor 26 outputs gaseous refrigerant or drop below the temperature of water in tank 36 .
- Selection of the target temperature may depend on the configuration of system 12 .
- Heat exchanger 38 cools refrigerant flowing through its coil (toward a lowest temperature equal to the temperature of water in the water heater tank) but removes heat from the refrigerant at a rate slower than the condenser's heat removal rate. Moreover, the heat exchanger's heat transfer capacity declines as the water heater's water temperature rises and approaches the refrigerant temperature.
- the target temperature for refrigerant exiting outdoor unit 14 is too high, the residual heat retained within the refrigerant flow path (due to the heat exchanger's failure to remove the heat) increases flow path pressure and, therefore, the work done by compressor 26 , for no offsetting heat transfer gain at the water heater or the conditioned air, thereby reducing system efficiency.
- setting the target temperature tool low reduces the heat exchanger's ability to transfer heat to the water heater tank.
- the target temperature is set to the highest temperature from which heat exchanger 38 can successfully bring refrigerant to the tank water temperature at any point in the tank's water temperature range between the water heater's low and high set points. Since the heat exchanger's heat transfer capacity is lower at other tank water temperatures, selection of this target results in some residual heat remaining in the refrigerant flow path as the tank's water temperature moves from this maximum point, but this cost may be acceptable in order to allow the heat exchanger its maximum heat transfer capacity.
- control system 20 downloads a range of temperature targets corresponding to changing water heater temperatures determined at calibration, and controller 25 continuously updates the target temperature in response to temperature data from the control system as water heater water temperature changes.
- control system initially downloads a target temperature equal to a predetermined temperature increment above the present tank water temperature. As tank water temperature rises, the control system increases the target temperature, up to the maximum target temperature.
- the predetermined increment is selected at system configuration and can be set as desired.
- control system 20 When the control system receives a signal from the water heater temperature sensor (either directly or through the water heater controller) indicating a need for water heating, control system 20 first determines the air conditioning mode (i.e. providing conditioned air to the conditioned space, or not providing conditioned air to the conditioned space, and if providing conditioned air in embodiments where the system both heats and cools, whether in air-heating or air-cooling configuration) in which the air conditioning system presently exists. As described below, control system 20 may have calibrated data sets for some or all of its air conditioning operation modes that represent a comparison of system efficiency when relying on the refrigerant heat exchanger or, alternatively, on the water heater's inherent heat source.
- the air conditioning mode i.e. providing conditioned air to the conditioned space, or not providing conditioned air to the conditioned space, and if providing conditioned air in embodiments where the system both heats and cools, whether in air-heating or air-cooling configuration
- control system If the control system has no data sets for its present air conditioning mode, it activates the water heater heat source and relies on that heat source to fully heat the water, without utilization of the heat exchanger. If it does have data sets for the present air conditioning mode, the control system identifies (1) ambient air temperature as detected from a temperature sensor at outdoor unit 14 that communicates with the control system, (2) indoor air temperature as detected by the indoor thermostat, and (3) water tank temperature as detected by the tank temperature sensor.
- control system 20 applies this input data to the air-conditioning-mode-dependent data sets which, given the specific operating parameter values represented by the input data, provide a ratio value representing a comparison of system efficiency (at these parameter values) when relying on the refrigerant heat exchanger and, alternatively, when relying on the water heater's inherent heat source. Based on this comparison, control system 20 selects between the two heating options, sets the system valves accordingly, and provides corresponding control signals to the water heater. Water heating continues, utilizing the selected heat source, but the control system repeatedly monitors these three input variables and correspondingly re-assesses the efficiency comparison based on the data sets.
- the control system deactivates the presently active heat source and activates the other heat source.
- the control system continues to monitor the variables, and continues to monitor for a change in chosen heat source that persists for the predetermined time period, and changes the heat source if that condition occurs. In this manner, the choice of heat source can change multiple times, as conditions change, before the water heater reaches its high set point.
- control system When the control system detects that the water heater has reached the high set point, the control system deactivates the then-active heat source and does not reactivate either heat source until receiving a water temperature signal indicating the tank's water temperature has dropped below the water heater's low set point, at which point the cycle repeats.
- the control system always assumes that use of the refrigerant heat exchanger is more efficient at low water heater temperatures, and so always initially utilizes the heat exchanger.
- the data set represents a comparison of system efficiency between two conditions: (1) air conditioning system and water heater operation when the refrigerant heat exchanger is active and the water heater heat source is inactive, and (2) air conditioning system and water heater operation when the refrigerant heat exchanger is inactive and the water heater heat source is active.
- overall system efficiency may be defined as the system's coefficient of performance, or COP.
- the COP may be described as the ratio of heating or cooling energy (BTU/hr or Watts) provided to the conditioned air plus heating energy (BTU/hr or Watts) moved into the water heater water, divided by energy (BTU/hr or Watts) consumed by the air conditioning system and water heater in providing such energy to the conditioned air and the water heater water.
- the energy input to the water and conditioned air, and energy consumed may depend on the electrical and mechanical configuration of the air conditioning and water heating system. For a given system, however, this consideration is a constant and can be accommodated in the calibration process as described herein. Relevant parameters that can vary, however, are:
- the air conditioning and water heating system (e.g. as illustrated in FIGS. 1-3 , FIGS. 4-7 , or FIGS. 8-13 ) is constructed and installed in conditions under which the defining variables can be controlled.
- the outdoor unit is operatively installed at a location at which it is possible to both operate the outdoor unit and vary the ambient temperature.
- the indoor unit is installed at a location separate from the outdoor unit at which it is possible to vary the indoor (conditioned space) ambient temperature.
- the water heater is disposed at a location at which the water heater water temperature can be controlled independently of the outdoor unit and indoor unit ambient temperatures.
- each system is then calibrated for each possible combination of the first two variables.
- the system does not have an air heating mode, and in its inactive mode the system valves are not configurable to permit use of the refrigerant heat exchanger.
- this system can operate selectively between the refrigerant heat exchanger and the water heater heat source only in its air cooling mode. Accordingly, a data set will exist only for the air-cooling mode, and the system would need efficiency calibration only under the following two conditions:
- Each of the systems described with respect to FIGS. 4-7 and FIGS. 8-13 can operate selectively between the refrigerant heat exchanger and the water heater heat source in any of its three air conditioning modes, and thus can be calibrated under the following six conditions:
- each variable can be varied over a respective range of values that would be reasonably expected to occur in the system's use.
- the system is operated in the calibration environment while varying the three variables and measuring or estimating the components of the system's COP. That is, for combinations of the three variables over their assumed operative ranges, the system determines and records system COP.
- the resulting data set is stored or otherwise accessible to control system 20 / 70 / 120 . Accordingly, after completing the calibration process for each of the dual variable (selected water heater heat source/air conditioning mode) configurations for a given system, the control system has, for each configuration, a COP data set from which COP can be defined with knowledge of the values for the three defining variables (outdoor ambient air, water tank water temperature, and indoor temperature).
- the control system In a given system's operation, the control system always knows the system's air conditioning mode, and it receives values for the three defining variables from corresponding sensors.
- a temperature sensor at the outdoor unit provides outdoor ambient temperature.
- the system thermostat provides indoor temperature
- the water heater temperature sensor provides water temperature.
- the control system receives a signal from the water heater temperature system indicating a need for water heating.
- the control system has a data set for each of the possible operating conditions, corresponding to selected water heater heat source and air conditioning mode. If the system is operating in one of the air conditioning modes for which a COP data set exists (e.g. any of the three air conditioning modes for the systems of FIGS.
- the control system retrieves the two data sets (one for refrigerant heat exchanger, and one for water heater water source) corresponding to that air conditioning mode, detects the actual defining variable values from the corresponding sensor inputs, and determines the COP value defined by the three variables for each of the two data sets. If the ratio of the COP for the system utilizing the refrigerant heat exchanger to the COP for the system utilizing the water heater heat source is equal to or greater than 1.0, the control system activates the refrigerant heat exchanger (i.e. with regard to the embodiment of FIG.
- control system 1 opens valve 44 , closes valve 50 , opens valve 40 , and instructs controller 25 to control fan 24 speed to maintain the target refrigerant level) and deactivates the water heater heat source, else if the ratio is less than 1.0, the control system deactivates the refrigerant heat exchanger and activates the water heater heat source.
- the control system continuously monitors the three defining variables. As long as the water heater water temperature is below the water heater's high set point, the control system repeatedly (e.g. every ten seconds) measures the three variables and recalculates the ratio. If the ratio changes state (i.e.
- the control system deactivates the presently active water heater heat source and activates the other water heater heat source.
- the control system thereafter continues to repeatedly read the defining variable values, re-determine the ratio, and change the water heat source if so indicated by a persistent ratio. This process continues until the water heater temperature reaches the high set point, at which point the control system deactivates both water heater heat sources, and takes no further water heating action until the water temperature signal indicates that the water heater water temperature has again fallen to or below the water heater's low set point, at which point the cycle repeats.
- control system selects the water heater heat source based on the system COP comparison as described above, but with the additional qualification that even if the COP comparison continues to favor selection of refrigerant heat exchanger, if that selection persists continuously for at least a predetermined period of time, e.g. thirty minutes, the control system will activate the water heater heat source and deactivate the refrigerant heat exchanger and thereafter allow the water heater heat source to heat the water heater water up to the water heater's high set point, without consideration of comparative system efficiency. Since the refrigerant heat exchanger is typically unable to bring the water heater to its final high set point alone, this modification to the process protects against system dedication to the refrigerant heat exchanger under conditions in which the heat exchanger cannot bring the water to the final set point.
- control system continuously monitors the COP comparison, as described above, and switches to the water heater heat source when the ratio drops below 1.0 and persists below that level for at least the predetermined period of time. Also, recognizing the likelihood that, once the COP comparison transitions the heat source to the water heater heat source, subsequent COP comparison would likely continue to select the water heater heat source, then once the control system switches to the water heater heat source, the control system no longer examines COP, instead maintaining activation of the water heater heat source through the end of water heating. In this embodiment, the control system may continue to monitor water heater temperature following the switch to the water heater heat source or, alternatively, relinquish control of the water heater heating cycle to the water heater controller to complete the cycle, as discussed above.
- control system 20 may store water temperature values received from the water heater's temperature sensor over a predetermined period of time, thereby determining actual change in water temperature. Since the control system also knows the volume of water in the water heater, the control system can determine the corresponding BTU/hr and convert that number to Watts.
- control system can determine whether the air handler fan has been active over the predetermined period of time, and since the control system knows the air handler's capacity, the control system can estimate the volume of air that the air handler has moved into the conditioned space. The control system also measures the conditioned space temperature from the thermostat signals, and based on the temperature change in the conditioned space and the estimated volume of air moved into the conditioned space within the predetermined period of time, the control system can estimate BTU/hr over that period, within an approximately 10% accuracy. Again, the control system can convert this number to Watts.
- certain components of the COP calculation do not exist. For example, where the air conditioning mode is inactive, there is no energy moved into or out of the conditioned space.
- the denominator of the COP calculation is the energy consumed by the system in contributing the energy represented by the numerator. This, in turn, is the energy used by the compressor, the coil fans, and the water heater over the predetermined time.
- Compressor power utilization may be directly measured in calibration by a watt meter or by continuously measuring compressor suction pressure, discharge pressure and suction gas temperature, in view of the compressor's performance curves. Fan power can be measured by a watt meter but can be estimates or assumed based on lab testing.
- the overall air conditioner/water heater circuit 10 a schematically illustrated in FIG. 3 is identical to the system 10 described above with respect to FIGS. 1 and 2 , with the exceptions that (1) an additional water heater 18 a , having either electric or gas heating apparatus associated therewith, but without an associated coiled tube refrigerant-to-water heat exchanger, is connected in series with the previously-described water heater 18 such that water exiting water heater 18 via pipe 56 flows through the additional water heater 18 a and is then discharged therefrom through a hot water outlet pipe 56 a , and (2) water heater 18 is not provided with electric or gas heat, but receives only refrigerant heat via its tubing heat exchanger portion 38 , thus functioning solely as a water pre-heating device.
- Water heater 18 a may correspond in capacity to water heater 18 as shown in FIGS. 1 and 2 , which is for example a forty to fifty gallon electric or gas water heater.
- the water heater 18 of FIG. 3 may be of a larger, smaller, or similar capacity.
- the configuration shown in FIG. 3 emphasizes the advantages of the refrigerant flow heat exchanger when water tank water temperature is low.
- the two tank configuration allows hot water to be stored when the air conditioning system 12 is running (in cooling or heating modes) during times when there is little or no demand for hot water, thereby providing additional low cost hot water capacity during periods of time when the demand for hot water is high. It also improves the efficiency of the air conditioning system compared to the single tank arrangement described above with respect to FIGS. 1 and 2 , since water in pre-heating tank 18 ( FIG. 3 ) will usually be at a lower temperature than water in the main tank during periods of time when there is little demand for hot water.
- the system does not use a comparison of efficiencies to control when to actuate and de-actuate the water heating heat exchanger 38 shown in FIG. 3 . Since the refrigerant heat exchanger is not proximate the same water heater that is heated by the water heater heat source, the efficiency comparison described above with respect to FIGS. 1 and 2 (and below with respect to FIGS. 4-7 and 8 - 13 ), is not applicable. Rather, water heater 18 a heats under its independent heat source, and the air conditioning system activates the refrigerant heat exchanger up to a predetermined set point temperature of the pre-heated tank 18 . The set point is set to a level below the temperature of the compressor output temperature, but it is otherwise selectable by the operator. A pre-heating tank may also be used with the air conditioning systems described below with respect to FIGS. 4-7 and 8 - 13 .
- FIGS. 4-7 An air conditioning system 60 embodying one or more principles of the present invention is schematically depicted in FIGS. 4-7 and includes (1) a heat pump 62 having an outdoor coil unit 64 and an indoor coil unit 66 , and (2) an associated water heater 68 which, representatively, may be a gas-fired or electric water heater.
- heat pump 62 is in an air cooling-only mode.
- heat pump 62 is in an air cooling mode and further provides supplemental, refrigerant-based water pre-heating to water heater 68 .
- FIG. 6 heat pump 62 is in an air heating-only mode.
- FIG. 4-7 An air conditioning system 60 embodying one or more principles of the present invention is schematically depicted in FIGS. 4-7 and includes (1) a heat pump 62 having an outdoor coil unit 64 and an indoor coil unit 66 , and (2) an associated water heater 68 which, representatively, may be a gas-fired or electric water heater.
- heat pump 62 is in an air cooling-only mode.
- FIG. 5
- heat pump 62 is in an air heating mode and further provides supplemental, refrigerant-based water pre-heating to water heater 68 .
- the various functions of air conditioning system 60 are controlled by a schematically depicted electronic control circuit 70 (shown only in FIG. 4 ) which operates various subsequently described components of system 60 .
- outdoor coil unit 64 includes a coil 72 and associated fan 74 , and a compressor 76 .
- Coil 72 and compressor 76 are coupled, as shown, by a refrigerant tubing circuit 78 having line portions 80 and 82 , to indoor unit coil 84 and to a heat conductive copper tube that is spiral-wrapped around a metal tank portion 86 of water heater 68 and serves as a refrigerant-to-tank water heat exchanger 88 for water heater 68 .
- Outdoor unit 64 has a reversing valve 90 , an electronically controlled regulator valve 92 , an expansion valve 94 , and a check valve 93 (which can be considered as the expansion valve's inherent check valve) connected as shown in tubing circuit 78 and operatively linked to electronic control system 70 .
- Indoor coil unit 66 has a normally closed solenoid valve 98 and a normally closed solenoid valve 100 connected across a check valve 109 as shown in tubing circuit 78 and operatively linked to electronic control system 70 .
- the indoor unit also has an expansion valve 110 , and the valve 100 / 109 / 110 assembly can be replaced by a parallel expansion/check valve as indicated at 93 / 94 .
- Water heater 68 has a temperature sensor 102 , an electronically controlled regulator valve or normally closed solenoid valve 104 , a normally open solenoid valve 106 , and a normally closed solenoid valve 108 connected as shown in tubing circuit 78 and operatively linked to electronic control system 70 .
- electronic control system 70 sets the previously described valve components in tubing circuit 78 in a manner such that compressor 76 causes refrigerant discharged therefrom to flow, via tubing portion 80 of tubing circuit 78 , sequentially through condenser coil 72 to water heater 68 , evaporator coil 84 , and back to the compressor. More specifically, as hot gaseous refrigerant flows out from compressor 76 on an output line 91 , control system 70 maintains solenoid valve 92 closed, so that all of the compressor's output refrigerant flows to reversing valve 90 .
- Control system 70 sets reversing value 90 to direct the gaseous refrigerant flow from line 91 to tubing portion 80 and thereby to condenser coil 72 . Since none of the refrigerant bypasses the condenser coil through valve 92 in this mode, all of the hot refrigerant from the compressor condenses in coil 72 and flows therefrom via check valve 93 out of this outdoor unit and to the indoor water heater.
- control system 70 maintains solenoid valve 104 closed and solenoid valve 106 open, and the refrigerant bypasses heat exchanger 88 through open solenoid valve 106 .
- the liquid refrigerant then flows through tubing portion 80 , through check valve 109 and expansion valve 110 (the control system maintains solenoid valves 100 , 98 , and 108 closed, and a check valve 111 blocks flow from left to right in the perspective of FIG. 4 ) and into evaporator coil 84 .
- the expansion valve lowers pressure of the liquid refrigerant, allowing the refrigerant to change phase from liquid to gas in the evaporator coil and draw required heat energy from air flowing over coil 84 due to the air handler fan, to thereby cool air in the conditioned space.
- positive and negative pressure contributed by compressor 76 in the refrigerant tubing line is sufficient so that the now-gaseous refrigerant flows back to compressor 76 over tubing line 82 through reversing valve 90 , which fluidly connects input tubing line 82 to a compressor input tubing line 95 .
- a temperature sensor (not shown) of water heater 68 sends an output signal to electronic control system 70 indicating that the water temperature of water in tank 68 has reached or fallen below the water heater's low set point temperature (as stored in memory at electronic control system 70 ), and if the COP comparison favors the refrigerant heat exchanger, the control system repositions water heater regulator valve 104 and normally open solenoid valve 106 such that the refrigerant flows through heat exchanger 88 and back into tubing portion 80 , thereby adding refrigerant heat to the tank water, to expansion valve 110 .
- valves 104 , 106 , and 92 are the same as those for valves 44 , 50 , and 40 , as discussed above with respect to FIG. 2 .
- valves 108 and 100 remain closed, as refrigerant flows through their respective opposing check valves, and valve 98 remains closed.
- Refrigerant flowing through coil 84 changes phase to a gas, as discussed above with respect to FIG. 4 , and gaseous refrigerant returns to compressor 76 via tubing 82 and 95 .
- fan 74 is controlled by a variable fan speed controller (see FIG. 2 ) that is, in turn, responsive to a pre-programmed target temperature in water-heating mode to control the speed of fan 74 so that the refrigerant flowing from coil 72 and bypass valve 92 maintain the desired target temperature in tubing 80 , as described above with regard to the embodiment of FIGS. 1 and 2 .
- the target temperature maybe selected as discussed above.
- control system 70 may select the water heating source based on the COP comparison (data sets exist for the air conditioning modes of this embodiment) or may default to selection of the refrigerant heat exchanger to heat the water heater when the control system receives a temperature signal from the water heater indicating a need to heat water. Regardless of the method or of the heat source chosen, the control system thereafter continuously re-assesses the COP comparison and selects between the two alternative water heating sources based thereon, as described above.
- control system may change the system's operation modes between air cooling of the conditioned space and air heating of the conditioned space (or actuation from one mode to the other from start up), or to the inactive mode, based on operator control of the system or automatically.
- the control system enters an air heating mode, and referring now FIG. 6 , the control system changes reversing valve 90 so that the refrigerant flowing from the compressor through tubing 91 flows through valve 90 to tubing 82 that connects to indoor coil 84 .
- Valve 98 remains closed.
- Coil 84 receiving the hot gaseous refrigerant from compressor 76 , now acts as condenser, cooling the refrigerant so that it changes phase back to a liquid.
- the liquid refrigerant bypasses expansion valve 110 through its internal check valve and flows through now-open solenoid valve 100 around check valve 109 .
- Control system 70 maintains valve 106 open and valves 104 and 108 closed. Since check valve 111 and closed valve 108 otherwise block the refrigerant's flow into heat exchanger 88 , refrigerant from coil 84 flows through valve 106 and through tubing 80 to outdoor unit 64 . The control system maintains valve 92 closed. Thus, all refrigerant from the indoor unit flows through expansion valve 94 and into outdoor coil 72 .
- Expansion valve 94 (which is bypassed by its internal check valve 93 when the system operates in air cooling modes) lowers the refrigerant's pressure, causing coil 72 to act as an evaporator that draws heat from air passing over the coil as a result of operation of fan 74 .
- the now-warmer refrigerant flows from coil 72 to expansion valve 90 , which directs the refrigerant flow to the compressor's input tubing line 95 .
- control system 70 decides whether to activate the heat exchanger or the water heater heat source, e.g., based on the data sets/COP comparison as described above, or by default to the heat exchanger followed by the data sets/COP comparison. Assuming the control system initially activates the heat exchanger, the control system appropriately adjusts valves 104 , 106 , and 108 in a manner such that the refrigerant flow to water heater 68 flows through coiled tubing heat exchanger 88 . More specifically, control system 70 closes valve 106 and valve 92 and opens valves 104 , 108 , 100 , and 98 .
- indoor unit 66 includes an air handling unit having a fan that draws air over coil 84 .
- unit 66 also includes a variable speed fan control unit 115 in communication with control system 70 and a temperature sensor 117 that detects refrigerant temperature in the flow of refrigerant combined from the output of coil 84 and bypass valve 98 .
- heat exchanger coil 88 acts as a sub-cooling or sub-condensing coil, sharing the condensing function with the system condenser, the difference between the two modes of operation being that in air heating mode, coil 84 , rather than coil 72 , is the system condenser.
- the system in air heating/water heating mode diverts some of the hot gaseous refrigerant from compressor 76 to coil 88 , bypassing the condensing coil, in order to contribute heat to the heat exchanger. And as in the air cooling mode, this is accomplished in the air heating mode by a valve that bypasses the condenser coil, in this instance valve 98 . That is, valve 98 serves the function in air heating/water heating mode that valve 92 serves in air cooling/water heating mode.
- valve 98 in air heating/water heating mode allows hot gaseous refrigerant to flow through the bypass path, but because refrigerant flowing through condenser coil 84 is cooled, and thus has lower flow resistance than the hot refrigerant, more refrigerant tends to flow through the condenser coil than through the bypass when the air handler fan is operating at its normal speed.
- control system 70 when control system 70 actuates system 60 to operate in air heating/water heating mode, the control system instructs variable fan speed controller 115 to variably control the air handler fan speed in response to temperature of the combined refrigerant flow detected at 117 to maintain the refrigerant flow at 117 at a target temperature that is pre-programmed to controller 115 and/or control system 70 .
- the target temperature in air-heating mode may be selected independently of the air-cooling mode target temperature, as system conditions can be different.
- the air handler fan While the system actuates refrigerant heat exchanger 88 , the air handler fan generally slows in speed, thereby increasing resistance to refrigerant flow through the condenser coil and forcing more refrigerant through bypass valve 98 .
- the bypass refrigerant remains in a hot, gaseous state so that the combination of gaseous refrigerant from valve 98 and liquid refrigerant from coil 84 is in a dual-phase state as it flows to heat exchanger 88
- This refrigerant flows through open valve 108 , around check valve 111 , and through heat exchanger coil 88 . This transfers heat from the refrigerant to the water tank and completes the condensing process, so that the refrigerant leaving coil 88 through open valve 104 is in a fully liquid state.
- the liquid refrigerant continues its flow through tubing 80 and valve 94 , around check valve 93 , to expansion valve 113 and evaporator coil 72 . From the evaporator coil, warmer, gaseous refrigerant flows through tubing 80 , reversing valve 90 , and input tubing 95 to compressor 76 , and the cycle repeats.
- Control system 70 makes the COP comparison as described above to determine when to alternatively operate refrigerant heat exchanger 88 or the water heater heat source. As when the system is operating in air cooling mode, the use of refrigerant heat exchanger 88 in air heating mode will generally be more efficient when the water in tank 86 is at a lower temperature. Thus, when control system 70 receives a signal from the water heater temperature sensor that the water heater is at or below its low set point temperature, control system 70 may default to operation of refrigerant heat exchanger 88 and thereafter continuously examines the efficiency comparison to determine when to switch to the water heater's operation.
- the target temperature to which fan controller 17 controls the refrigerant input to the heat exchanger is typically below the water heater's high set point temperature, this typically means that the refrigerant flow heat exchanger acts as a pre-heater and that final heating is effected by the water heater heat source.
- control system 70 may therefore switch from use of heat exchanger 88 to the use of the water heater's heat source earlier in air heating/water heating mode than in air cooling/water heating mode.
- variable speed fan controller 115 and sensor 117 may be omitted from the system, and the air handler fan may operate at normal speed during actuation of heat exchanger 88 in air heating mode. This avoids the reduction in system efficiency caused by decrease in fan speed, although because of the resulting reduction in diversion of hot refrigerant to the heat exchanger through valve 98 , the heat exchanger would correspondingly contribute less heat to the water heater, thereby reducing system efficiency. It will therefore be appreciated that the decision whether to utilize variable fan speed, and if so, also the selection of the target refrigerant temperature at the output of the bypass valve and the condenser coil, will influence system efficiency and, therefore, the balance between use of refrigerant heat exchanger 88 and the water heater heat source. It will also be understood that, in both air heating and air conditioning modes, decisions regarding use of fan reduction can be made, and operating parameter values optimized, through calibration of the particular air conditioning system.
- control system actuates the refrigerant heat exchanger when the air conditioning system is operating either in an air cooling mode or an air heating mode.
- control system only actuates the heat exchanger during an active mode of the air conditioning system, but in other embodiments the control system also actuates the refrigerant heat exchanger when the system is in an inactive mode, i.e. when running neither in air cooling mode nor air heating mode. In such embodiments, and referring for example to the system of FIGS.
- control system 70 receives a signal from the water heater temperature sensor indicating that water in the water heater has reached or fallen below the heater's low temperature set point, the control system decides whether to activate the heat exchanger or the water heater heat source, e.g., based on the COP comparison as described above, or by default to the heat exchanger. Assuming the decision is to activate the heat exchanger, the control system arranges the valves in the air conditioning system so as to operate in air heating/water heating mode, as discussed above with respect to FIG. 7 , and operates the air conditioning system in the manner described above with regard to FIG. 7 , except that the control system deactivates the air handler fan so that no air is drawn across coil 84 and no conditioned air is provided to the conditioned space.
- variable fan speed controller is inoperative. This tends to force a greater volume of hot refrigerant from the compressor through bypass valve 98 , but the refrigerant flow is thereafter the same as discussed above with regard to FIG. 7 .
- the control system does operate fan 24 , since the evaporator function is needed to complete the refrigerant cycle. Since the evaporator function is needed, the control system does not select an air cooling set up, as such arrangement would cause conditioned air to be forced into the conditioned space.
- compressor 76 may be a variable speed compressor so that control system 70 may reduce compressor speed when heating water with the heat exchanger but not conditioning air.
- control system 70 would lower a variable speed compressor to operate at a lower capacity, e.g. approximately 10,000 BTU/hr in a typical residential configuration.
- control system 70 in a water heating-only mode again determines whether and when to switch between heating water with the refrigerant heat exchanger and heating water with the water heater heat source based on the COP comparison.
- the refrigerant heat exchanger coil is disposed downstream of the system condenser. In the embodiments discussed below with respect to FIGS. 8-13 , however, the heat exchanger coil is disposed upstream from the system condenser, between the system condenser and the compressor. In these embodiments, the heat exchanger coil reduces heat of the hot gaseous refrigerant output by the compressor (and transfers this heat to the water heater), but it does not condense the refrigerant to a liquid phase. Because the heat exchanger coil receives hot refrigerant directly from the compressor, it is unnecessary to bypass the compressor output around the condenser or, therefore, to reduce condenser fan speed in order to encourage such bypass flow.
- the system condenser fan operates at normal speed whether or not the refrigerant heat exchanger is active. This tends to increase system efficiency as compared to the embodiments described above with regard to FIGS. 1-7 . In certain environments, however, the embodiments described with regard to FIGS. 1-7 may be more convenient to install, particularly into an existing air conditioning system as a retrofit.
- FIG. 8 schematically depicts an air conditioning/water heater system 110 embodying principles of an embodiment of the present invention.
- System 110 includes (1) an air conditioning system 112 having an outdoor coil unit 114 and an indoor coil unit 116 , and (2) and associated water heater 118 which, representatively, may be a gas-fired or electric water heater.
- air conditioning system 112 is arranged so that it may operate alternatively in air heating and air cooling modes, and may therefore also be described as a heat pump.
- the various functions of the air conditioning/water heater system 110 are controlled by a schematically depicted electronic control circuit 120 (shown only in FIG. 8 ) that operates various subsequently described components of overall system 110 .
- Outdoor unit 114 includes an outdoor coil 122 and associated fan 137 and a compressor 126 .
- Condenser coil 122 and compressor 126 are coupled, as shown, by a refrigerant tubing circuit having a line portion 130 between coil 122 and a reversing valve 140 through an indoor unit coil 134 and expansion valve 160 , a line portion 131 between reversing valve 140 and compressor 126 via a heat conductive copper tube that is spiral-wrapped around a metal tank portion 136 of water heater 118 and serving as a refrigerant-to-tank water heat exchanger 138 for water heater 118 , and a line portion 132 between reversing valve 140 and each of coil 122 and compressor 126 .
- outdoor unit 114 includes an electronically controlled regulator valve 142 , an expansion valve 153 at an input to outdoor coil 122 (bypassed when receiving outflow from coil 122 ), solenoid valves 144 and 154 , and a check valve 161 .
- Valves 154 , 144 , 142 , and 140 are in electrical communication with electronic control system 120 , which controls the actuation of these valves as discussed herein.
- electronic control system 120 sets valves 154 , 144 , and 140 in the overall tubing circuit in a manner such that compressor 126 causes refrigerant discharged therefrom to flow, via tubing portion 131 , to the entry point of a tubing loop that includes heat exchanger 138 wrapped around tank 136 of water heater 118 .
- Electronic control system 120 has closed valve 154 and opened valve 144 , so that hot gaseous refrigerant flowing from compressor 126 bypasses heat exchanger 138 and flows directly to reversing valve 140 .
- Control system 120 has set reversing valve 140 so that the reversing valve directs this refrigerant flow, via tubing line 132 , to outdoor coil 122 , which condenses the refrigerant in cooperation with fan 137 as discussed above.
- the refrigerant exits coil 122 via tubing line 130 (bypassing expansion valve 163 ) and enters indoor coil 134 via expansion valve 160 .
- expansion valve 160 lowers the pressure of the refrigerant in coil 134 so that coil 134 functions as an evaporator.
- An air handler fan 135 adjacent coil 134 causes air to flow over coil 134 and into the conditioned space.
- the refrigerant's change of phase in the evaporator coil from liquid to gas draws heat energy from this air, thereby causing the re-circulating air to cool the conditioned space.
- the now gaseous and warmer refrigerant flows from coil 134 via tubing portion 130 to reversing valve 140 , which directs the gaseous refrigerant flow, via tubing portion 132 , back to compressor 126 , and the cycle repeats.
- the control system decides whether to activate the heat exchanger or the water heater heat source, e.g., based on the COP comparison as described above or by default to the heat exchanger. Assuming the decision is to activate the heat exchanger, the electronic control system closes valve 144 and opens valve 154 , thereby activating refrigerant heat exchanger 138 . Reversing valve 140 remains in the same setting as discussed with regard to FIG.
- hot gaseous refrigerant output from compressor 126 flows to heat exchanger 138 of water heater 118 via tubing portion 131 , bypassing valve 144 , and ultimately to reversing valve 140 via check valve 161 .
- the refrigerant flows from the reversing valve to outdoor condenser coil 122 , and then to expansion valve 160 , indoor coil 134 , reversing valve 140 , and back to compressor 126 , as discussed above with respect to FIG. 9 .
- the control system continuously assesses the data sets/COP comparison. If the resulting ratio drops below 1.0, the control system deactivates initially selected heat source and activates the other heat source.
- system 110 (with heat exchanger 138 active) is generally more efficient than the system described above with respect to FIG. 2 or FIG. 5 , in that reduction of fan speed for condenser coil 122 is unnecessary in air conditioning/water heating mode. Counterbalancing that positive efficiency effect is the longer refrigerant tubing line 131 needed between the compressor and the water heater, but this effect is often offset and even overcome by the increase in efficiency caused by the cooling effect the refrigerant experiences as it travels through heat exchanger 138 .
- operation of the system illustrated in FIG. 11 results in a positive system efficiency ratio, as compared to operation of the system and water heater heat source independently of each other, for a longer rise in temperature of water in water heater tank 136 than does the systems described above with regard to FIG. 2 and FIG. 5 .
- the water heater receives hot gaseous refrigerant directly from compressor 126 , without need to regulate the refrigerant temperature being directed to the heat exchanger to a lower target temperature, as described above with regard to FIGS. 2 and 5 , the heat exchanger illustrated in FIG. 11 can transfer more heat to the water heater, thereby maintaining a positive contribution to system efficiency over a longer temperature range.
- Electronic control system 120 monitors pressure at the output of compressor 12 and, if the monitored pressure exceeds a predetermined pressure (provided by the compressor manufacturer or by user selection, for example after a calibration process), control system 120 may switch valve 142 from a closed to an opened state, allowing refrigerant flow through a tubing portion 145 , bypassing heat exchanger 138 and condenser coil 122 , to the lower pressure of the evaporator.
- control system 120 may selectively open proportional valve 142 whenever the compressor output pressure reaches or exceeds 550 psi. As will be understood in the context of the present disclosure, this reduces system efficiency, in that it diverts heat from transfer to the water heater and reduces the evaporator efficiency, and accordingly valve 142 is metered to minimize its impact.
- control system 120 changes, either by manual or electronic control, from air cooling to air heating modes, without water heating and with reference to FIG. 10 , control system 120 closes valve 154 , opens valve 144 , and sets reversing valve 140 to direct refrigerant flow from tubing line 131 to indoor coil 134 via tubing line 130 and to direct refrigerant flow from coil 122 via line 132 back to compressor 126 via tubing line 132 .
- hot gaseous refrigerant flows from compressor 126 through tubing line 131 and open valve 144 , bypassing heat exchanger 138 due to closed valve 154 .
- Reversing valve 140 directs the gaseous refrigerant to indoor coil 134 via tubing line 130 .
- Coil 134 acts as a condenser coil, cooling and condensing the refrigerant to liquid phase as air handler fan 135 moves air over the coils and into the conditioned space.
- the re-circulating building air draws heat energy from the refrigerant as it condenses, thereby providing a heating effect to the conditioned space.
- the now-liquid refrigerant flows to coil 122 through expansion valve 163 .
- the expansion valve lowers the refrigerant's pressure, causing outdoor coil 122 to act as an evaporator, in which the refrigerant changes phase to a gas and draws heat energy from outdoor ambient air drawn over the coils by outdoor unit fan 137 .
- the now-warm gaseous refrigerant flows from coil 122 to reversing valve 140 , which directs the refrigerant flow back to compressor 126 via tubing line 132 , and the cycle repeats.
- control system 120 decides whether to activate the heat exchanger or the water heater heat source, e.g. based on the data sets/COP comparison as described above, or by default to the heat exchanger. Assuming the decision is to activate the heat exchanger, the control system closes valve 144 and opens valve 154 , thereby activating heat exchanger 138 by including the heat exchanger and its related portion of tubing section 131 in the refrigerant flow loop.
- this causes hot gaseous refrigerant to flow from compressor 126 to and through heat exchanger coil 138 via tubing section 131 and thereafter to reversing valve 140 via check valve 161 .
- the refrigerant's flow from reversing valve 140 , to indoor coil 134 , expansion valve 163 , outdoor coil 122 , reversing valve 140 , and back to compressor 126 occurs as discussed above with regard to FIG. 10 .
- FIGS. 9 and 11 illustrate the transition from air cooling-only mode to air cooling/water heating mode
- FIGS. 10 and 12 illustrate the transition from air heating-only mode to air heating/water heating mode.
- the electronic control system thereafter continuously monitors the COP comparison of system efficiency with operation of refrigerant water heater 138 , and without operation of the water heater's heat source, to system efficiency with refrigerant flow heat exchanger 138 deactivated and the water heater's inherent heat source activated. If this ratio drops below 1.0 as the system operates, the electronic control system deactivates refrigerant flow heat exchanger 138 (by closing valve 154 an opening valve 144 ), and activates the water heater's inherent heat source.
- electronic control system 120 continues to monitor the water temperature output signal, and if the ratio rises above 1.0 and persists for a predetermined time will switch back to activation of the refrigerant flow heat exchanger.
- the water heater heat source may be deactivated by a control system on the water heater that is independent of electronic control system 120 , or the heat source may be deactivated by control system 120 .
- the temperature of refrigerant flowing from compressor 126 is also a limiting factor, as compared to the water heater's high set point.
- refrigerant flow heat exchanger 138 is always a pre-heating device. If the compressor refrigerant output temperature is higher than the water heater high set point, it is possible for refrigerant flow heat exchanger 138 to bring the water heater fully to its high set point.
- operation of refrigerant flow heat exchanger 138 in an air heating/water heating mode results in the removal of heat from the refrigerant flow at heat exchanger 138 that might otherwise be removed at coil 134 for contribution to conditioned air for the conditioned space. This may result in a reduced system efficiency as compared to the operation of the system in an air cooling/water heating mode, thereby resulting in a shorter duration of operation of the refrigerant heat exchanger in air heating/water heating mode than in a air cooling/water heating mode.
- Valve 142 is operated by control system 120 in this mode in the same manner as discussed above with respect to FIGS. 9 and 11 .
- electronic control system 120 receives a signal from the water heater water temperature sensor indicating that water heating is needed, when system 110 is in neither an air heating mode nor an air cooling mode, control system 120 sets valves 154 , 144 , and 140 to an air heating configuration, as discussed above with regard to FIG. 12 , but does not activate air handler fan 135 because there is no call from the indoor thermostat to provide conditioned air to the conditioned space.
- Refrigerant flows through the refrigerant loop as described with regard to FIG. 12 .
- compressor 126 is a variable speed compressor
- the control system changes the compressor's output to a lower level, e.g. 10,000 BTU/hr.
- electronic control system 120 opens bypass valve 142 .
- bypass valve 142 may further decrease system efficiency, thereby increasing the likelihood of a switch to water heater activation.
- each of the embodiments described with regard to FIGS. 1-13 can be operated based on a comparison of system efficiency when using the refrigerant heat exchanger to system efficiency when using the water heater's heat source, and relying on that comparison as the deciding factor whether to utilize the heat exchanger throughout the water heater's heat cycle.
- the electronic control system upon receiving a signal from the water heater temperature sensor indicating a need to heat water, actuates the refrigerant heat exchanger coil and maintains the heat exchanger coil active until the temperature signal reaches a predetermined point.
- This predetermined cut-off point may be determined through testing and comparison of system efficiencies alternatively utilizing the refrigerant flow heat exchanger and the water heater heat source. That is, the systems are operated under each of the alternative arrangements, and under similar operating conditions. System efficiencies are compared, and a temperature cut off is selected based on the comparison. Furthermore, temperature may be measured at various points in the water heater, as should be understood in the art, and in certain embodiments the electronic control system responds to water temperature taken at the lower portion of the lower tank.
- the electronically controlled regulator valves may be replaced with fixed orifice solenoid valves, and the flow of hot refrigerant to the water heater refrigerant-to-water heat exchanger coils may instead be regulated by compressor discharge (head) pressure using an outdoor or indoor fan speed controller which is, in turn, controlled by the sensed water temperature in the water heater tank.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- Physics & Mathematics (AREA)
- Combustion & Propulsion (AREA)
- Chemical & Material Sciences (AREA)
- Sustainable Development (AREA)
- Life Sciences & Earth Sciences (AREA)
- Air Conditioning Control Device (AREA)
- Heat-Pump Type And Storage Water Heaters (AREA)
- Other Air-Conditioning Systems (AREA)
- Central Heating Systems (AREA)
- Steam Or Hot-Water Central Heating Systems (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
An apparatus for heating water has a tank for storing water and an air conditioning system that defines a refrigerant flow path through which refrigerant flows. The refrigerant flow path passes through the heat exchanger so that refrigerant heat is contributed to the tank. A control system controls operation of the water heating apparatus.
Description
- The present application claims the benefit of the filing date of provisional U.S. Patent Application No. 61/779,087, filed Mar. 13, 2013, the entire disclosure of which is hereby incorporated herein for all purposes.
- Various apparatus and methods have been previously proposed for pre-heating water in a water heater tank using refrigerant from air conditioning apparatus such as an air conditioner with a non-reversible refrigerant circuit or a heat pump having a reversible refrigerant circuit. However, such previously proposed apparatus and methods have often proven to be undesirably complex and expensive for use in many applications.
- An embodiment of an apparatus for heating water according to the present invention includes a tank for storing water, and a heater exchanger in thermal communication with the tank and configured to receive refrigerant and transfer heat therefrom to the tank. An air conditioning system has an air handler actuatable to move an air flow through an air flow path into a conditioned space. A refrigerant path has a first portion that passes through the air flow path and a second portion that passes through the heat exchanger. A pump is disposed in the refrigerant path and is actuatable to move refrigerant through the refrigerant path. A control system is in operative communication with the air handler to control actuation of the air handler and is in operative communication with the pump to control actuation of the pump. In a first mode of operation, the control system actuates the air handler to move the air flow through the air flow path and actuates the pump to move refrigerant through the first portion of the refrigerant path and the second portion of the refrigerant path. In a second mode of operation, the control system maintains the air handler in an inactive state and actuates the pump to move refrigerant through the first portion of the refrigerant path and the second portion of the refrigerant path.
- In a further embodiment, an apparatus for heating water includes a tank for storing water and a temperature sensor in thermal communication with water in the tank and configured to output a first signal corresponding to temperature of the water. A heat exchanger is in thermal communication with the tank and is configured to receive refrigerant and transfer heat therefrom to the tank. An air conditioning system has an air handler actuatable to move an air flow through an air flow path into a conditioned space. A refrigerant path has a first portion that passes through the air flow path and a second portion that passes through the heat exchanger. A valve system within the refrigerant path controls refrigerant flow to the first portion and the second portion and is selectively configurable to alternatively allow refrigerant flow through the second portion and block refrigerant flow through the second portion. A pump is disposed in the refrigerant path and is actuatable to move refrigerant through the refrigerant path. A thermostat is operable to measure ambient temperature in the conditioned space and to output a second signal corresponding to ambient temperature in the conditioned space. A control system is in operative communication with the tank to receive the first signal, is in operative communication with the air handler to control actuation of the air handler, is in operative communication with the pump to control actuation of the pump, is in operative communication with the valve system to selectively allow refrigerant flow through the second portion and block refrigerant flow through the second portion, and is in operative communication with the thermostat to receive the second signals. In response to the first and second signals, in a first mode of operation, the control system actuates the air handler to move the air flow through the air flow path, actuates the pump to move refrigerant through the refrigerant path, and configures the valve system to allow refrigerant flow through the second portion. In a second mode of operation, the control system maintains the air handler in an inactive state, actuates the pump to move refrigerant through the refrigerant path, and configures the valve system to allow refrigerant flow through the second portion. In a third mode of operation, the control system actuates the air handler to move the air flow through the air flow path, actuates the pump to move refrigerant through the refrigerant path, and configures the valve system to block refrigerant flow through the second portion.
- In a further embodiment, an apparatus for heating water has a tank for storing water and having a heat source. A heat exchanger is in thermal communication with the tank and is configured to receive refrigerant and transfer heat therefrom to the tank. An air conditioning system has an air handler actuatable to move an air flow through an air flow path into a conditioned space. A refrigerant path has a first portion that passes through the air flow path and a second portion that passes through the heat exchanger. A pump is disposed in the refrigerant path and is actuatable to move refrigerant through the refrigerant path. A plurality of sensors respectively output signals representative of respective system operating parameters. A control system is in operative communication with the tank to control operation of the heat source, is in operative communication with the air handler to control actuation of the air handler, is in operative communication with the sensors to receive the respective signals, and is in operative communication with the refrigerant path to control refrigerant flow. In response to the signals from the sensors, the control system selectively allows or blocks refrigerant flow through the second portion and selectively actuates the water heater heat source.
- In a still further embodiment, an apparatus for heating water has a tank for storing water and having a heat source. A heat exchanger is in thermal communication with the tank and is configured to receive refrigerant and transfer heat therefrom to the tank. An air conditioning system has an air handler actuatable to move an air flow through an air flow path into a conditioned space. A refrigerant path has a first portion that passes through the air flow path and a second portion that passes through the heat exchanger. A pump is disposed in the refrigerant path and is actuatable to move refrigerant through the refrigerant path. A valve system within the refrigerant path controls refrigerant flow in the first portion and the second portion and is selectively configurable to alternatively allow refrigerant flow through the second portion and block refrigerant flow through the second portion. A plurality of sensors each outputs a respective signal representative of a respective system operating parameter that varies in a predetermined relationship with operating efficiency of at least one of the tank and the air conditioning system. A control system is in operative communication with the tank to control operation of the heat source, is in operative communication with the air handler to control actuation of the air handler, is in operative communication with the sensors to receive the respective signals, and is in operative communication with the valve system to control refrigerant flow. In response to the respective signals from sensors, the control system selectively actuates the valve system to allow refrigerant flow through the second portion or block refrigerant flow through the second portion and selectively actuates the water heater heat source.
- The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate one or more embodiments of the present invention.
- Aspects of the present invention can be better understood with reference to the following drawings. The components in the drawings are not necessarily to scale. An enabling disclosure of the present invention, including the best mode thereof, is set forth in the specification, which makes reference to the appended drawings, in which:
-
FIG. 1 is a schematic view of an air conditioning system according to an embodiment of the present invention, with an air conditioning system providing only conditioned space air conditioning; -
FIG. 2 is a schematic diagram of the system as inFIG. 1 , but with the air conditioning system providing conditioned space air and providing refrigerant heat to a water heater; -
FIG. 3 is a schematic diagram of the system as inFIG. 2 , but with the air conditioning system providing refrigerant heat to one of two water heater tanks in a two water heater tank arrangement; -
FIG. 4 is a schematic diagram of a an air conditioning system according to an embodiment of the present invention, with an air conditioning system providing only conditioned space air cooling; -
FIG. 5 is a schematic diagram of the system as inFIG. 4 , but with the air conditioning system providing conditioned space air and providing refrigerant heat to a water heater; -
FIG. 6 is a schematic diagram of the system as inFIG. 4 , but with the air conditioning system providing conditioned space air heating without providing refrigerant heat to a water heater; -
FIG. 7 is a schematic diagram of the system as inFIG. 4 , but with the air conditioning system providing conditioned space air and providing refrigerant heat to a water heater; -
FIG. 8 is a schematic diagram of an air conditioning system according to an embodiment of the present invention; -
FIG. 9 is a schematic diagram of the system as inFIG. 8 , but with the air conditioning system providing conditioned space air cooling without providing refrigerant heat to a water heater; -
FIG. 10 is a schematic diagram of the system as inFIG. 8 , but with the air conditioning system providing conditioned space air heating without providing refrigerant heat to a water heater; -
FIG. 11 is a schematic diagram of the system as inFIG. 8 , but with the air conditioning system providing conditioned space air and providing refrigerant heat to a water heater; -
FIG. 12 is a schematic diagram of the system as inFIG. 8 , but with the air conditioning system providing conditioned space air and providing refrigerant heat to a water heater; and -
FIG. 13 is a schematic diagram of the system as inFIG. 8 , but with the air conditioning system providing refrigerant heat to a water heater without providing conditioned space air. - Repeat use of reference characters in the present specification and drawings is intended to represent same or analogous features or elements of embodiments of the present invention.
- Reference will now be made in detail to presently preferred embodiments of the invention, one or more examples of which are illustrated in the accompanying drawings. Each example is provided by way of explanation of the invention, not limitation of the invention. In fact, it will be apparent to those skilled in the art that modifications and variations can be made in such examples without departing from the scope or spirit thereof. For instance, features illustrated or described as part of one embodiment may be used on another embodiment to yield a still further embodiment. Thus, it is intended that the present invention covers such modifications and variations as come within the scope of the appended claims and there equivalents.
- As used herein, the terms “air conditioning” apparatus, system, etc. encompass apparatus useable to change the temperature of air being delivered to a conditioned space and having an associated refrigerant circuit. Thus, an “air conditioning” apparatus or system may comprise, without limitation, (1) an air conditioning unit (or “air conditioner”) having a non-reversible refrigerant circuit that may be used to cool air delivered to a conditioned space, or (2) a heat pump having a reversible refrigerant circuit that may be used to heat or cool air delivered to a conditioned space.
- Residential and commercial air conditioning systems capture heat at some point in the refrigerant's continuous cycle and transfer the heat to a point inside or outside the building, depending upon whether the system is functioning in a cooling mode or, if capable of dual modes, in a heating mode. In carrying out principles of one or more embodiments of the present invention, a portion of that heat may be captured and used to heat water in the building's water heater to a temperature at or, more often, below a high set point temperature of the water heater. An electric element or gas burner in the water heater may provide additional heat to bring the water temperature up to the water heater's high set point temperature.
- An air conditioning/
water heater system 10 embodying principles of an embodiment of the present invention is schematically depicted inFIGS. 1 and 2 and includes (1) anair conditioning system 12 having an outdoorcondensing coil unit 14 and an indoor evaporatingcoil unit 16, and (2) an associatedwater heater 18 which, representatively, may be a gas-fired or electric water heater. InFIG. 1 ,air conditioning system 12 is arranged so that it operates in an air cooling mode only, and inFIG. 2 is in an air cooling mode and further provides supplemental, refrigerant-based heat towater heater 18. The various functions of air conditioning/water heater system 10 are controlled by a schematically depicted electronic control circuit 20 (shown only inFIG. 1 ) that operates various subsequently described components of theoverall system 10. - As should be understood, an air conditioning system, from the standpoint of refrigerant flow, comprises a closed loop of refrigerant flowing among a compressor (i.e. a pump), a condenser coil, and an evaporator coil. In so-called split systems, one of the two coils is disposed inside the enclosure that is receiving conditioned air (the conditioned space, e.g. a building interior space), in association with an air handler, while the other coil is disposed outside the enclosure of the conditioned space, in the ambient environment. The compressor may be inside or outside the enclosure, such as a building interior, but is typically outside in a housing that also encloses the outside coil. In a system configured only to cool, the outdoor coil is the condenser, and the indoor coil is an evaporator. Refrigerant flows from the compressor, to the outdoor condenser coil, to the indoor evaporator coil, and back to the compressor. The outdoor unit includes a fan that draws ambient air across the condenser coils to draw heat from the coils. As will be understood, the refrigerant acquires this heat in part from the indoor air at the evaporator as the liquid refrigerant evaporates in the coil in response to the influence of an expansion valve at the coil's input. As the system's air handler fan moves the building's recirculating air over the evaporator coils as the refrigerant changes phase from liquid to gas, the refrigerant removes energy (i.e. heat) from the indoor air, thereby cooling the air as it is forced back into the building's conditioned space. The warm refrigerant gas then flows from the evaporator coil to the compressor, which receives the gas and pumps it back to the condenser, adding pressure and heat. In embodiments in which the air conditioning system operates as a heat pump, refrigerant lines between the compressor and the condenser, and between the compressor and the evaporator, pass through a reversing valve so that, when switching from cooling mode to a heating mode, the control system actuates the reversing valve to direct the compressor output to the indoor coil, rather than to the outdoor coil. The roles of the indoor and outdoor coils reverse from those the coils have in air cooling modes, but the sequence of compressor-condenser-evaporator-compressor remains.
- As noted, the condenser cools the refrigerant, thereby dissipating the refrigerant's acquired heat (from the evaporator and the compressor) to the ambient environment via the air flow that the fan moves over the coil. The temperature reduction in the condenser also reduces the refrigerant's volume, in turn reducing its pressure, but the refrigerant flow path length and tubing dimensions, and the compressor's size and strength, are selected so that sufficient positive and negative pressure remain at the condenser's output and input to continue refrigerant flow to the evaporator and therefrom back to the compressor. The selection of such system components and operating parameters to enable desired heat transfer and recirculating refrigerant flow through the flow circuit should be well understood in this art. While it should be understood that the air conditioning systems described below are designed to provide sufficient heat transfer and pressure to maintain system operation, these variables are not discussed further herein.
- One or more embodiments of the present invention described herein insert into the refrigerant path a cooling coil that is proximate a water heater to be in thermal communication with the water heater tank and thereby transfer heat from the flowing refrigerant to water in the tank. The addition of the cooling coil does not disrupt the air conditioning system's underlying compressor-condenser-evaporator-compressor sequence, but it is nonetheless encompassed within the present disclosure to use a single coil, wrapped around a water heater tank and functioning as both the heat exchanger and the air conditioning system condenser, in conditions where the heat exchanger provides sufficient cooling for the air conditioning system's condenser needs and where the air conditioning system does not require air flow over the condenser. Thus, although the present disclosure primarily discusses examples having a fan-driven system condenser and a distinct water heater heat transfer coil, it should be understood that other arrangements fall within the present disclosure.
- Although the presently-described embodiments are discussed in the context of split-type air conditioning systems, it should be understood that the present disclosure encompasses air conditioning systems in which the condenser and evaporator coils may be located in the same housing.
-
Control system 20 may comprise a programmable logic controller (PLC) that operates as the general system controller. Housed, for example, withoutdoor unit 14, the PLC communicates with and controls (via suitable electrical connections, relays, power sources, and other electromechanical connections, as should be understood in this art) the actuation and operation of the components described herein, including but not limited to the compressor, outdoor coil fan, indoor coil fan, and all electrically controlled valves. As such, the control system communicates with and controls the air conditioning system, including the valve system within the refrigerant flow path that, in conjunction with the compressor (also controlled by the control system) controls refrigerant flow. The reference to connections betweencontrol system 20 and each ofoutdoor unit 14,indoor unit 16, and water heater 18 (and betweencontrol system 70 and each ofoutdoor unit 64,indoor unit 66, andwater heater 68, and betweencontrol system 120 and each ofoutdoor unit 114,indoor unit 116, and water heater 138) encompass such communications and control. Such communication may also encompass communication between the control system and a temperature sensor at the outdoor unit, which provides a signal to the control system corresponding to temperatures of the outdoor unit's ambient environment. Furthermore,control system 20 receives input signals from one or more thermostats in the building's conditioned space that provide instructions regarding whether to activate the air conditioning system, deactivate the air conditioning system, actuate the air handler fan, operate the system in air cooling mode, and (where the air conditioning system is a heat pump) operate the system in air heating mode. The thermostat, being located in the conditioned space and including a temperature sensor, may also output to the control system a signal corresponding to temperature of the conditioned space. The operation of thermostats in generating such instructions should be well understood and is, therefore, not discussed further herein. The thermostat may be considered a part ofcontrol system 20, and, in any event, functions typically performed by the thermostat can be shared or performed bycontrol system 20. The reference to communication betweencontroller 20 and indoor unit 16 (and betweencontrol system 70 andindoor unit 66, and betweencontrol system 120 and indoor unit 116) encompass such communications between the control system and the thermostat(s), as well as communication between the control system and the air handler and between the control system and the water heater. The control system activates and deactivates the air handler, based on the air conditioning system programming in response to signals from the thermostat and possibly signals from sensors indicating system operating parameters, as should be understood. In an inactive state, the air handler does not force air into, draw air into, or otherwise move air through the conditioned space. As discussed herein, actuation of the air conditioning system may refer to activation of the compressor to move refrigerant through the refrigerant path, activation of the condenser fan, and activation of the air handler (fan), in certain embodiments. But as discussed herein, in some circumstances the air conditioning system may be actuated without activating the air handler. In that sense, the control system activates the air conditioning system while maintaining the air handler in an inactive state. - Reference to communication between
controller 20/50/120 andindoor unit 16/66/116 also encompasses communication between the control system and the water heater, e.g. the water heater controller or, particularly where the water heater controller's functions are incorporated by the control system, between the control system and the water heater temperature sensor(s) and heat source(s). As should be understood,water heater 18 may include an electronic controller (not shown) that can receive manual or electronic instructions to activate and deactivate a water heater and can respond to such instructions as well as activating and deactivating the water heater in response to pre-programmed set point temperatures. The water heater's high and low set point temperatures are typically capable of manual or electronic setting by the operator and/or at installation. Once set, the water heater's controller monitors the output of one or more temperature sensors in thermal communication with water inside the water heater and compares the water temperature with the predetermined set points. If the water heater is in an inactive state, and if the water tank temperature is above the water heater's low set point, the water heater controller takes no action until the water tank temperature reaches or falls below the low set point. At this point, the water heater controller activates the water heater's internal heat source, which begins to heat the water. The water heater controller continues to receive and monitor water temperature signals from the one or more water heater temperature sensors, and maintains the water heater heat source active until the controller receives a signal from the one or more temperature sensors indicating that the water heater temperature has exceeded the high set point. The water heater goes back to an inactive mode and does not reactivate until manually activated or until the signal from the one or more temperature sensors indicates that the water temperature has again fallen to or below the low set point. - In the presently described embodiments, however, the water heater controller passes the water heater temperature sensor signals or corresponding data to control
system 20/70/120, which then determines whether to heat the water heater with refrigerant heat or with the water heater's inherent heat source, as described above. If, or when, the control system decides to operate the water heater heat source, the control system sends a corresponding signal to the water heater controller, which actuates the heat source. The water heater controller may thereafter monitor water temperature and deactivate the heat source when the temperature reaches the high set point, or it may continue to pass the temperature signal or data to the control system, which makes the decision when to deactivate the water heater heat source and sends an appropriate instruction signal to the water heater controller. Still further, the water heater controller may be omitted, and thecontrol system 20/70/120 put in direct communication with the water heater temperature sensor(s) and heat source control (i.e. activation and deactivation control) in order to perform the functions described herein. The reference to communication betweencontroller 20 and water heater 18 (and betweencontrol system 70 andwater heater 68, and betweencontrol system 120 and water heater 138) encompass such communications between the control system and the water heater controller or, particularly where the water heater controller's functions are incorporated by the control system, between the control system and the water heater temperature sensor(s) and heat source(s). - Similarly, as described below,
control systems variable fan controllers control systems indoor units 14/64 and 16/66 reflect such communications. Still further, however, the functions of the variable fan controllers may also be incorporated entirely within the control system, so that the fan controllers may be omitted and the control system communicates directly withtemperature sensors 27/117, or 42 or 46. - It will be understood from the present disclosure that the functions ascribed to control
system 20/70/120 may be embodied by computer-executable instructions of a program that executes on one or more computers, for example embodied by a residential or commercial split system air conditioning system controller. Generally, program modules include routines, programs, components, data structures, etc., that perform particular tasks and/or implement particular abstract data types. Moreover, those skilled in the art will appreciate that the systems/methods described herein may be practiced with various controller configurations, including programmable logic controllers, simple logic circuits, single-processor or multi-processor systems, as well as personal computers, hand-held computing devices, microprocessor-based or programmable consumer or industrial electronics, and the like. Aspects of these functions may also be practiced in distributed computing environments, for example in so-called “smart home” arrangements and systems, where tasks are performed by remote processing devices that are linked through a local or wide area communications network to the components otherwise illustrated in the Figures. In a distributed computing environment, programming modules may be located in both local and remote memory storage devices. Thus,control system 20 may comprise a computing device that communicates with the system components described herein via hard wire or wireless local or remote networks. - A controller that could effect the functions described herein could include a processing unit, a system memory and a system bus. The system bus couples the system components including, but not limited to, system memory to the processing unit. The processing unit can be any of various available programmable devices, including microprocessors, and it is to be appreciated that dual microprocessors, multi-core and other multi processor architectures can be employed as the processing unit.
- Software applications may act as an intermediary between users and/or other computers and the basic computer resources of
electronic control system 20, as described, in suitable operating environments. Such software applications include one or both of system and application software. System software can include an operating system that acts to control and allocate resources ofcontrol system 20. Application software takes advantage of the management of resources by system software through the program models and data stored on system memory. - The controller may also, but does not necessarily, include one or more interface components that are communicatively coupled through the bus and facilitate interaction with the control system. By way of example, the interface component can be a port (e.g., serial, parallel, PCMCIA, USC, or FireWire) or an interface card, or the like. The interface component can receive input and provide output (wired or wirelessly). For instance input can be received from devices including but not limited to a pointing device such as a mouse, track ball, stylus, touch pad, key pad, touch screen display, keyboard, microphone, joy stick, gamepad, satellite dish, scanner, camera, or other component. Output can also be supplied by
control system 20 to output devices via the interface component. Output devices can include displays (for example cathode ray tubes, liquid crystal display, light emitting diodes, or plasma) whether touch screen or otherwise, speakers, printers, and other components. In particular, by such means,control system 20 received inputs from, and directs outputs to, the various components with whichcontrol system 20 communicates, as described herein. - In general, the control system receives signals from the thermostat, the water heater, and possibly temperature sensors or other operating parameter sensors that are not part of the thermostat or water heater. The controller activates or deactivates the air conditioning system to provide or stop the provision of conditioned air to a conditioned space in response to the thermostat signals. It decides whether to activate a water heating source in response to the water heating signal, and it decides which water heating heat source to utilize in response to the water heater signals and the operating parameter signals (which may include the thermostat signal) and in some instances in response to the air conditioning mode in which the air conditioning system exists. The apparatus for carrying out these functions, and the manner of their operation, are described below.
- Referring initially to
FIG. 1 ,outdoor condensing unit 14 includes acondenser coil 22, an associatedcondenser fan 24, and acompressor 26. The condenser coil and compressor are coupled, as shown, by arefrigerant tubing circuit 28 and liquidrefrigerant line portions unit evaporator coil 34 and to a heat conductive refrigeration tube spiral-wrapped around ametal tank portion 36 ofwater heater 18 and serving as a refrigerant to tankwater heater exchanger 38 forwater heater 18. Although a single coil is illustrated, multiple parallel coils may be utilized to reduce pressure drop through the heat exchanger. Thus, it should be understood that reference to a heat exchanger “coil” encompasses one or multiple coils, in series or in parallel. It will also be understood that the coils may be covered in insulation. - Operatively linked to
electronic control system 20 are (1) an electronically controlledregulator valve 40 with an associatedrefrigerant temperature sensor 42 installed as shown inrefrigerant tubing circuit 28 within condensingunit 14, (2) an electronically controlledregulator valve 44 and an associatedrefrigerant temperature sensor 46 installed as shown inrefrigerant tubing circuit 28 betweenline 32 and (adjacent to) arefrigerant inlet 48 ofheat exchanger coil 38, and (3) a normallyopen solenoid valve 50 installed in arefrigerant bypass line 32 a betweenheat exchanger inlet 48 and a heatexchanger refrigerant outlet 52. As illustrated inFIG. 1 , water to be heated flows intowater heater tank 36 via awater inlet pipe 54 and, in response to a heated water demand, is discharged fromtank 36 via a hotwater supply pipe 56. -
FIGS. 1-7 illustratetemperature sensors temperature sensors fan controllers temperature sensors temperature sensor 27. These sensors should, therefore, be understood as alternatives tosensor 27 and may be omitted in the presence ofsensor 27. - Further, the Figures illustrate various electronically controlled valves as normally open or normally closed valves, whereas other valves are illustrated as electronically controlled proportional valves. As will be understood, the normally open or normally closed valves transition between open or closed states, whereas the proportional valves can be used to meter fluid flow if desired. In the examples discussed herein, all the electronically controlled valves transition between fully open and fully closed states, and it is thus encompassed within the present disclosure that all valves may be non-proportional valves. It should also be understood, however, that the use of proportional valves to meter fluid flow, for example via the condenser bypass valves, is encompassed within the scope of the present disclosure.
- An
expansion valve 58 is disposed inline 32 at an inlet toindoor coil 34. As should be understood, an expansion valve receives a fluid input at a high pressure and, depending on the settings within the valve, outputs the fluid at a lower pressure. This allows pressurized refrigerant entering coil 34 (when used as an evaporator) to drop in pressure in the evaporator coil and change phase from a liquid to a gas. - Under the conditions illustrated in
FIG. 1 ,control system 20 receives a signal from controller or a temperature sensor inwater heater 18 indicating that the tank's water temperature is above the water heater's low set point, which is stored in the control system's memory. That is, no water heating is called for. Assume, also, thatcontrol system 20 has received a signal from the building's thermostat (not shown) requiring the air conditioning system to provide cool air to the conditioned space. Withair conditioning system 12 accordingly in an air cooling-only mode, without need for the control system to also select and actuate a water heating heat source (e.g. the water heater's heat source or refrigerant heat transferred to the water intank 36 via heat exchanger 38), gaseous refrigerant flows from evaporatorcoil 34 tocompressor 26 viasuction line 30.Compressor 26 pumps the gaseous refrigerant forward, increasing the refrigerant's pressure and temperature and causing the now-hotter refrigerant gas to flow throughcondenser coil 22.Control system 20 actuates fan 24 (at a constant speed) via a variablefan speed control 25 to thereby push or draw air over the condenser coils, causing the gaseous refrigerant to cool incoil 22 and thereby change phase from a gas to a liquid. This draws heat energy from the refrigerant into the moving air, thereby dissipating heat from the refrigerant (and, therefore, from the conditioned space) into the ambient environment. Still under the pressure provided bycompressor 26, the now-liquid refrigerant flows from the output ofcondenser 22 to the split between the input line toheat exchanger 38 and the bypassline including valve 50.Control system 20 maintainsvalve 40, between the condenser and the compressor, closed. Since no water heating is called for,control system 20 maintainsvalve 44 closed andvalve 50 in its normally fully open position. This blocks refrigerant flow to the heat exchanger coil, and liquid refrigerant exitingcondenser coil 22 therefore flows throughopen solenoid valve 50, bypassing waterheater heat exchanger 38, toexpansion valve 58.Expansion valve 58 drops the pressure of the liquid refrigerant as it entersevaporator coil 34. Within the evaporator, the refrigerant transitions to gaseous phase, drawing heat energy from air flowing overcoil 34, which is disposed in the air flow path generated by an air handler fan (the air flow path is illustrated schematically inFIG. 1 by the relationship ofcoil 34 and the illustrated fan). This cools the indoor air being re-circulated by the air handler, thereby cooling the conditioned indoor space. The now-warmer gaseous refrigerant discharged from evaporatorcoil 34 then returns tocompressor 26 viasuction line 30, and the cycle repeats. - As noted,
control system 20 controls the operation ofheat exchanger 38 in response to receipt of temperature information from a water heater controller or from a temperature sensor attank 36. As should be understood,water heater 18 typically operates between low and high temperature set points. In the presently-described embodiments,control system 20, rather than the water heater's independent control, responds to water heater water temperature when it falls below the water heater's low set point, selecting between the water heater's inherent heat source andheat exchanger 38 as the means by which to add heat to the water heater, depending upon which heat source results in higher overall system efficiency. The basis for this decision is discussed in more detail below. - Turning now to
FIG. 2 , whenwater heater 18 requires refrigerant heat (as determined by comparison of the value of a temperature signal from the non-illustrated temperature sensor in a bottom portion oftank 36 to the stored water tank low set point), control system 20 (FIG. 1 ) appropriately positions the various previously describedvalves traversing tubing circuit 28 from the outdoor unit to pass throughheat exchanger 38, thereby adding refrigerant heat to water intank 36, before flowing toevaporator coil 34. Whencontrol system 20 detects that heating responsibility should shift from the heat exchanger to the water heater heat source, or thatwater heater 18 no longer needs refrigerant heat, as described below, it returnsair conditioning system 12 to its air cooling-only mode, as discussed with regard toFIG. 1 , in which all of the refrigerant flow traversingtubing circuit 28 bypasses water heater coiledtube heat exchanger 38. - More specifically, when the control system receives a signal from the temperature sensor indicating water heating is needed, when
air conditioning system 12 is otherwise in an operative mode to provide conditioned air to a conditioned space, and when the control system initially actuates water heating byheat exchanger 38 rather than the water heater's inherent heat source,control system 20 switchesfan speed controller 25 from full speed (at whichfan 24 is operated during air cooling-only mode) to a variable speed mode (in whichfan speed controller 25 controls the speed offan 24 in response to atemperature sensor 27, as described below), opensvalve 44, closesvalve 50, and opensvalve 40. By openingvalve 44 and closingvalve 50, the control system directs the entirety of the refrigerant flow throughheat exchanger 38. The condenser coil, however, receives only part of the refrigerant flow output fromcompressor 26. By openingvalve 40 and allowing some of the refrigerant flow to bypass the condenser, the refrigerant flowing fromcondenser 22 andvalve 40 toheat exchanger 28 contains both cooler liquid and warmer gaseous refrigerant. That is, the refrigerant flow includes hot gaseous refrigerant that, but forbypass valve 40, would have cooled and condensed incoil 22 but is instead diverted tocoil 38, which in turn cools the refrigerant, condenses the gaseous refrigerant component of the dual phase refrigerant flow that reaches the heat exchanger, and transfers the removed heat to water withinwater heater tank 36. Accordingly,heat exchanger 38 may be considered a sub-condenser or sub-cooler of the overall condenser, as it completes the condensing function begun bycondenser coil 22. -
Valve 40, therefore, effectively diverts heat from the compressor output to the heat exchanger that the condenser would otherwise have removed. The amount of heat that the valve diverts is defined by the balance of refrigerant flow betweenvalve 40 andcoil 22. This balance is, in turn, defined by the speed offan 24. The bypass refrigerant flowing throughvalve 40 is warmer than the condensed refrigerant flowing throughcondenser coil 22. As should be understood, the cooler, condensed refrigerant presents less resistance to flow through the condenser coil than does the hot gaseous refrigerant throughbypass valve 40, even though the bypass valve path is much shorter in length. Thus, ifvalve 40 is opened to its fully open state whencondenser 22 is operating at its full capacity, most of the refrigerant fromcompressor 26 will flow through the condenser rather than the bypass valve, thereby delivering a relatively low amount of additional, diverted heat to the heat exchanger. To increase the refrigerant flow balance towardbypass valve 40,variable fan controller 25 reduces the speed offan 24 when water heating is needed. This reduces the rate at which air flows over the condenser coils, thereby reducing the rate at which refrigerant in the condenser coil cools and correspondingly increasing the resistance to refrigerant flow. This, in turn, increases refrigerant flow through the bypass valve and increases the heat contributed to the heat exchanger. - At system set up,
control system 50 downloads a target temperature to fancontroller 25. When, in system operation,controller 25 receives a signal fromcontroller 20 indicating that water heating mode has begun,fan controller 25 ceases full speed fan operation and compares the output oftemperature sensor 27 to the target temperature. If thesensor 27 temperature is above the target temperature,controller 25 increases the speed offan 24, which thereby draws air over (and cools) the refrigerant in the coil at a higher rate, and reduces the amount of hot bypass refrigerant flowing throughvalve 40. If thesensor 27 temperature is below the target temperature,controller 25 decreases the speed offan 24, thereby reducing the heat removed from the refrigerant, and increasing its flow resistance, to thereby allow more hot gaseous refrigerant to bypass the condenser coil. Thus, the target temperature represents the temperature at which the condenser/bypass combination provides refrigerant to the heat exchanger. The target temperature preferably does not exceed the temperature at whichcompressor 26 outputs gaseous refrigerant or drop below the temperature of water intank 36. - Selection of the target temperature may depend on the configuration of
system 12.Heat exchanger 38 cools refrigerant flowing through its coil (toward a lowest temperature equal to the temperature of water in the water heater tank) but removes heat from the refrigerant at a rate slower than the condenser's heat removal rate. Moreover, the heat exchanger's heat transfer capacity declines as the water heater's water temperature rises and approaches the refrigerant temperature. If the target temperature for refrigerant exitingoutdoor unit 14 is too high, the residual heat retained within the refrigerant flow path (due to the heat exchanger's failure to remove the heat) increases flow path pressure and, therefore, the work done bycompressor 26, for no offsetting heat transfer gain at the water heater or the conditioned air, thereby reducing system efficiency. On the other hand, setting the target temperature tool low reduces the heat exchanger's ability to transfer heat to the water heater tank. One way of selecting a target temperature within these boundaries is to operate the system in a pre-installation calibration process, testing the system's efficiency and heat transfer for various target temperatures within the possible temperature range and selecting the target temperature that balances these considerations to the user's preference. In one embodiment, the target temperature is set to the highest temperature from whichheat exchanger 38 can successfully bring refrigerant to the tank water temperature at any point in the tank's water temperature range between the water heater's low and high set points. Since the heat exchanger's heat transfer capacity is lower at other tank water temperatures, selection of this target results in some residual heat remaining in the refrigerant flow path as the tank's water temperature moves from this maximum point, but this cost may be acceptable in order to allow the heat exchanger its maximum heat transfer capacity. In a further embodiment,control system 20 downloads a range of temperature targets corresponding to changing water heater temperatures determined at calibration, andcontroller 25 continuously updates the target temperature in response to temperature data from the control system as water heater water temperature changes. In a still further embodiment, the control system initially downloads a target temperature equal to a predetermined temperature increment above the present tank water temperature. As tank water temperature rises, the control system increases the target temperature, up to the maximum target temperature. The predetermined increment is selected at system configuration and can be set as desired. - When the control system receives a signal from the water heater temperature sensor (either directly or through the water heater controller) indicating a need for water heating,
control system 20 first determines the air conditioning mode (i.e. providing conditioned air to the conditioned space, or not providing conditioned air to the conditioned space, and if providing conditioned air in embodiments where the system both heats and cools, whether in air-heating or air-cooling configuration) in which the air conditioning system presently exists. As described below,control system 20 may have calibrated data sets for some or all of its air conditioning operation modes that represent a comparison of system efficiency when relying on the refrigerant heat exchanger or, alternatively, on the water heater's inherent heat source. If the control system has no data sets for its present air conditioning mode, it activates the water heater heat source and relies on that heat source to fully heat the water, without utilization of the heat exchanger. If it does have data sets for the present air conditioning mode, the control system identifies (1) ambient air temperature as detected from a temperature sensor atoutdoor unit 14 that communicates with the control system, (2) indoor air temperature as detected by the indoor thermostat, and (3) water tank temperature as detected by the tank temperature sensor. The control system applies this input data to the air-conditioning-mode-dependent data sets which, given the specific operating parameter values represented by the input data, provide a ratio value representing a comparison of system efficiency (at these parameter values) when relying on the refrigerant heat exchanger and, alternatively, when relying on the water heater's inherent heat source. Based on this comparison,control system 20 selects between the two heating options, sets the system valves accordingly, and provides corresponding control signals to the water heater. Water heating continues, utilizing the selected heat source, but the control system repeatedly monitors these three input variables and correspondingly re-assesses the efficiency comparison based on the data sets. If the choice of heat source resulting from these changing variables changes from the then-currently active heat source to the other, and if that condition persists uninterrupted for some predetermined period of time, e.g. one minute, then the control system deactivates the presently active heat source and activates the other heat source. The control system continues to monitor the variables, and continues to monitor for a change in chosen heat source that persists for the predetermined time period, and changes the heat source if that condition occurs. In this manner, the choice of heat source can change multiple times, as conditions change, before the water heater reaches its high set point. When the control system detects that the water heater has reached the high set point, the control system deactivates the then-active heat source and does not reactivate either heat source until receiving a water temperature signal indicating the tank's water temperature has dropped below the water heater's low set point, at which point the cycle repeats. In a further embodiment, the control system always assumes that use of the refrigerant heat exchanger is more efficient at low water heater temperatures, and so always initially utilizes the heat exchanger. - The data set represents a comparison of system efficiency between two conditions: (1) air conditioning system and water heater operation when the refrigerant heat exchanger is active and the water heater heat source is inactive, and (2) air conditioning system and water heater operation when the refrigerant heat exchanger is inactive and the water heater heat source is active. For each condition, overall system efficiency may be defined as the system's coefficient of performance, or COP. The COP may be described as the ratio of heating or cooling energy (BTU/hr or Watts) provided to the conditioned air plus heating energy (BTU/hr or Watts) moved into the water heater water, divided by energy (BTU/hr or Watts) consumed by the air conditioning system and water heater in providing such energy to the conditioned air and the water heater water.
- As should be understood in this art, the energy input to the water and conditioned air, and energy consumed, may depend on the electrical and mechanical configuration of the air conditioning and water heating system. For a given system, however, this consideration is a constant and can be accommodated in the calibration process as described herein. Relevant parameters that can vary, however, are:
-
- Selected water heat source, i.e. the refrigerant heat exchanger or the water heater's inherent heat source;
- Air conditioning mode, i.e. (1) air cooling, (2) air heating, or (3) inactive (neither air cooling nor air heating);
- Outdoor ambient temperature;
- Water tank water temperature; and
- Indoor temperature.
- To calibrate the system, the air conditioning and water heating system (e.g. as illustrated in
FIGS. 1-3 ,FIGS. 4-7 , orFIGS. 8-13 ) is constructed and installed in conditions under which the defining variables can be controlled. The outdoor unit is operatively installed at a location at which it is possible to both operate the outdoor unit and vary the ambient temperature. The indoor unit is installed at a location separate from the outdoor unit at which it is possible to vary the indoor (conditioned space) ambient temperature. The water heater is disposed at a location at which the water heater water temperature can be controlled independently of the outdoor unit and indoor unit ambient temperatures. - Each system is then calibrated for each possible combination of the first two variables. Consider, first, the system described with respect to
FIGS. 1-3 . As is apparent from the discussion herein, the system does not have an air heating mode, and in its inactive mode the system valves are not configurable to permit use of the refrigerant heat exchanger. Thus, this system can operate selectively between the refrigerant heat exchanger and the water heater heat source only in its air cooling mode. Accordingly, a data set will exist only for the air-cooling mode, and the system would need efficiency calibration only under the following two conditions: -
- Air cooling space conditioning and operation of refrigerant heat exchanger; and
- Air cooling space conditioning and operation of water heater heat source.
- Each of the systems described with respect to
FIGS. 4-7 andFIGS. 8-13 can operate selectively between the refrigerant heat exchanger and the water heater heat source in any of its three air conditioning modes, and thus can be calibrated under the following six conditions: -
- Air cooling space conditioning and operation of refrigerant heat exchanger;
- Air cooling space conditioning and operation of water heater heat source;
- Air heating space conditioning and operation of refrigerant heat exchanger;
- Air heating space conditioning and operation of water heater heat source;
- Inactive air conditioning and operation of refrigerant heat exchanger; and
- Inactive air conditioning and operation of water heater heat source.
- Assume, then, that a given system is assembled in such a calibration environment, and operated sequentially in each of its possible conditions as noted above. In each condition, two of the five COP-relevant variables are fixed, and the remaining three variables (outdoor ambient temperature, water tank temperature, and indoor (conditioned space) temperature) can be controlled in the calibration environment. In particular, each variable can be varied over a respective range of values that would be reasonably expected to occur in the system's use. Given the three variables, and given the respective expected ranges for each, the system is operated in the calibration environment while varying the three variables and measuring or estimating the components of the system's COP. That is, for combinations of the three variables over their assumed operative ranges, the system determines and records system COP. For a given system, the resulting data set is stored or otherwise accessible to control
system 20/70/120. Accordingly, after completing the calibration process for each of the dual variable (selected water heater heat source/air conditioning mode) configurations for a given system, the control system has, for each configuration, a COP data set from which COP can be defined with knowledge of the values for the three defining variables (outdoor ambient air, water tank water temperature, and indoor temperature). - In a given system's operation, the control system always knows the system's air conditioning mode, and it receives values for the three defining variables from corresponding sensors. As noted, a temperature sensor at the outdoor unit provides outdoor ambient temperature. The system thermostat provides indoor temperature, and the water heater temperature sensor provides water temperature. Assume, then, that the system is operating in one of the three air conditioning modes, and the control system receives a signal from the water heater temperature system indicating a need for water heating. With calibration complete, the control system has a data set for each of the possible operating conditions, corresponding to selected water heater heat source and air conditioning mode. If the system is operating in one of the air conditioning modes for which a COP data set exists (e.g. any of the three air conditioning modes for the systems of
FIGS. 4-7 and 8-13, but only air cooling mode for the system ofFIGS. 1 and 2 ), the control system retrieves the two data sets (one for refrigerant heat exchanger, and one for water heater water source) corresponding to that air conditioning mode, detects the actual defining variable values from the corresponding sensor inputs, and determines the COP value defined by the three variables for each of the two data sets. If the ratio of the COP for the system utilizing the refrigerant heat exchanger to the COP for the system utilizing the water heater heat source is equal to or greater than 1.0, the control system activates the refrigerant heat exchanger (i.e. with regard to the embodiment ofFIG. 1 , opensvalve 44, closesvalve 50, opensvalve 40, and instructscontroller 25 to controlfan 24 speed to maintain the target refrigerant level) and deactivates the water heater heat source, else if the ratio is less than 1.0, the control system deactivates the refrigerant heat exchanger and activates the water heater heat source. The control system continuously monitors the three defining variables. As long as the water heater water temperature is below the water heater's high set point, the control system repeatedly (e.g. every ten seconds) measures the three variables and recalculates the ratio. If the ratio changes state (i.e. moves across the 1.0 threshold, thereby indicating a change in water heater heat source from the presently activated source) and persists in the changed state for more than a predetermined period of time, e.g. one minute, the control system deactivates the presently active water heater heat source and activates the other water heater heat source. The control system thereafter continues to repeatedly read the defining variable values, re-determine the ratio, and change the water heat source if so indicated by a persistent ratio. This process continues until the water heater temperature reaches the high set point, at which point the control system deactivates both water heater heat sources, and takes no further water heating action until the water temperature signal indicates that the water heater water temperature has again fallen to or below the water heater's low set point, at which point the cycle repeats. - In a further embodiment, the control system selects the water heater heat source based on the system COP comparison as described above, but with the additional qualification that even if the COP comparison continues to favor selection of refrigerant heat exchanger, if that selection persists continuously for at least a predetermined period of time, e.g. thirty minutes, the control system will activate the water heater heat source and deactivate the refrigerant heat exchanger and thereafter allow the water heater heat source to heat the water heater water up to the water heater's high set point, without consideration of comparative system efficiency. Since the refrigerant heat exchanger is typically unable to bring the water heater to its final high set point alone, this modification to the process protects against system dedication to the refrigerant heat exchanger under conditions in which the heat exchanger cannot bring the water to the final set point.
- It should be understood that variations in the heat source selection process are encompassed by the present disclosure. For example, it should be understood in view of the present disclosure that use of the refrigerant heat exchanger tends to be more efficient than use of the water heater heat source when the water heater water temperature is low. At the lower temperatures, the water heater draws more heat from the refrigerant flowing through the heat exchanger than at higher temperatures, thereby lessening the resistance that the heat exchanger coil provides to refrigerant flow and reducing system pressure. As the water heater water temperature is always at the water heater low set point when the control system initiates water heating, in one embodiment the control system defaults to operation of the refrigerant heat exchanger at cycle initiation, without reference to the COP comparison (assuming data sets exist for the existing air-conditioning mode). Thereafter, the control system continuously monitors the COP comparison, as described above, and switches to the water heater heat source when the ratio drops below 1.0 and persists below that level for at least the predetermined period of time. Also, recognizing the likelihood that, once the COP comparison transitions the heat source to the water heater heat source, subsequent COP comparison would likely continue to select the water heater heat source, then once the control system switches to the water heater heat source, the control system no longer examines COP, instead maintaining activation of the water heater heat source through the end of water heating. In this embodiment, the control system may continue to monitor water heater temperature following the switch to the water heater heat source or, alternatively, relinquish control of the water heater heating cycle to the water heater controller to complete the cycle, as discussed above.
- It will be understood in view of the present disclosure that various methodologies may be used to determine the components of the COP calculations during system calibration. To determine energy actually moved into the water heater water,
control system 20 may store water temperature values received from the water heater's temperature sensor over a predetermined period of time, thereby determining actual change in water temperature. Since the control system also knows the volume of water in the water heater, the control system can determine the corresponding BTU/hr and convert that number to Watts. - As should be understood in this art, precise determination of actual energy moved into or out of the conditioned air involves a determination of enthalpy change over the predetermined time period. While methods of making such measurements are known, they may also be unavailable or impractical. However, since the control system can determine whether the air handler fan has been active over the predetermined period of time, and since the control system knows the air handler's capacity, the control system can estimate the volume of air that the air handler has moved into the conditioned space. The control system also measures the conditioned space temperature from the thermostat signals, and based on the temperature change in the conditioned space and the estimated volume of air moved into the conditioned space within the predetermined period of time, the control system can estimate BTU/hr over that period, within an approximately 10% accuracy. Again, the control system can convert this number to Watts.
- In some instances, of course, certain components of the COP calculation do not exist. For example, where the air conditioning mode is inactive, there is no energy moved into or out of the conditioned space.
- The denominator of the COP calculation is the energy consumed by the system in contributing the energy represented by the numerator. This, in turn, is the energy used by the compressor, the coil fans, and the water heater over the predetermined time. Compressor power utilization may be directly measured in calibration by a watt meter or by continuously measuring compressor suction pressure, discharge pressure and suction gas temperature, in view of the compressor's performance curves. Fan power can be measured by a watt meter but can be estimates or assumed based on lab testing.
- The overall air conditioner/
water heater circuit 10 a schematically illustrated inFIG. 3 is identical to thesystem 10 described above with respect toFIGS. 1 and 2 , with the exceptions that (1) anadditional water heater 18 a, having either electric or gas heating apparatus associated therewith, but without an associated coiled tube refrigerant-to-water heat exchanger, is connected in series with the previously-describedwater heater 18 such that water exitingwater heater 18 viapipe 56 flows through theadditional water heater 18 a and is then discharged therefrom through a hotwater outlet pipe 56 a, and (2)water heater 18 is not provided with electric or gas heat, but receives only refrigerant heat via its tubingheat exchanger portion 38, thus functioning solely as a water pre-heating device.Water heater 18 a may correspond in capacity towater heater 18 as shown inFIGS. 1 and 2 , which is for example a forty to fifty gallon electric or gas water heater. Thewater heater 18 ofFIG. 3 may be of a larger, smaller, or similar capacity. - The configuration shown in
FIG. 3 emphasizes the advantages of the refrigerant flow heat exchanger when water tank water temperature is low. The two tank configuration allows hot water to be stored when theair conditioning system 12 is running (in cooling or heating modes) during times when there is little or no demand for hot water, thereby providing additional low cost hot water capacity during periods of time when the demand for hot water is high. It also improves the efficiency of the air conditioning system compared to the single tank arrangement described above with respect toFIGS. 1 and 2 , since water in pre-heating tank 18 (FIG. 3 ) will usually be at a lower temperature than water in the main tank during periods of time when there is little demand for hot water. - The system does not use a comparison of efficiencies to control when to actuate and de-actuate the water
heating heat exchanger 38 shown inFIG. 3 . Since the refrigerant heat exchanger is not proximate the same water heater that is heated by the water heater heat source, the efficiency comparison described above with respect toFIGS. 1 and 2 (and below with respect toFIGS. 4-7 and 8-13), is not applicable. Rather,water heater 18 a heats under its independent heat source, and the air conditioning system activates the refrigerant heat exchanger up to a predetermined set point temperature of thepre-heated tank 18. The set point is set to a level below the temperature of the compressor output temperature, but it is otherwise selectable by the operator. A pre-heating tank may also be used with the air conditioning systems described below with respect toFIGS. 4-7 and 8-13. - An
air conditioning system 60 embodying one or more principles of the present invention is schematically depicted inFIGS. 4-7 and includes (1) aheat pump 62 having anoutdoor coil unit 64 and anindoor coil unit 66, and (2) an associatedwater heater 68 which, representatively, may be a gas-fired or electric water heater. InFIG. 4 ,heat pump 62 is in an air cooling-only mode. InFIG. 5 ,heat pump 62 is in an air cooling mode and further provides supplemental, refrigerant-based water pre-heating towater heater 68. InFIG. 6 ,heat pump 62 is in an air heating-only mode. InFIG. 7 ,heat pump 62 is in an air heating mode and further provides supplemental, refrigerant-based water pre-heating towater heater 68. The various functions ofair conditioning system 60 are controlled by a schematically depicted electronic control circuit 70 (shown only inFIG. 4 ) which operates various subsequently described components ofsystem 60. - As shown in
FIGS. 4-7 ,outdoor coil unit 64 includes acoil 72 and associatedfan 74, and acompressor 76.Coil 72 andcompressor 76 are coupled, as shown, by arefrigerant tubing circuit 78 havingline portions indoor unit coil 84 and to a heat conductive copper tube that is spiral-wrapped around ametal tank portion 86 ofwater heater 68 and serves as a refrigerant-to-tankwater heat exchanger 88 forwater heater 68. -
Outdoor unit 64 has a reversingvalve 90, an electronically controlledregulator valve 92, anexpansion valve 94, and a check valve 93 (which can be considered as the expansion valve's inherent check valve) connected as shown intubing circuit 78 and operatively linked toelectronic control system 70.Indoor coil unit 66 has a normally closedsolenoid valve 98 and a normally closedsolenoid valve 100 connected across acheck valve 109 as shown intubing circuit 78 and operatively linked toelectronic control system 70. The indoor unit also has anexpansion valve 110, and thevalve 100/109/110 assembly can be replaced by a parallel expansion/check valve as indicated at 93/94.Water heater 68 has atemperature sensor 102, an electronically controlled regulator valve or normally closedsolenoid valve 104, a normallyopen solenoid valve 106, and a normally closedsolenoid valve 108 connected as shown intubing circuit 78 and operatively linked toelectronic control system 70. - Turning now to
FIG. 4 , withair conditioning system 60 in an air cooling-only mode,electronic control system 70 sets the previously described valve components intubing circuit 78 in a manner such thatcompressor 76 causes refrigerant discharged therefrom to flow, viatubing portion 80 oftubing circuit 78, sequentially throughcondenser coil 72 towater heater 68,evaporator coil 84, and back to the compressor. More specifically, as hot gaseous refrigerant flows out fromcompressor 76 on anoutput line 91,control system 70 maintainssolenoid valve 92 closed, so that all of the compressor's output refrigerant flows to reversingvalve 90.Control system 70sets reversing value 90 to direct the gaseous refrigerant flow fromline 91 totubing portion 80 and thereby tocondenser coil 72. Since none of the refrigerant bypasses the condenser coil throughvalve 92 in this mode, all of the hot refrigerant from the compressor condenses incoil 72 and flows therefrom viacheck valve 93 out of this outdoor unit and to the indoor water heater. - At the water heater,
control system 70 maintainssolenoid valve 104 closed andsolenoid valve 106 open, and the refrigerant bypassesheat exchanger 88 throughopen solenoid valve 106. The liquid refrigerant then flows throughtubing portion 80, throughcheck valve 109 and expansion valve 110 (the control system maintainssolenoid valves check valve 111 blocks flow from left to right in the perspective ofFIG. 4 ) and intoevaporator coil 84. As discussed above, the expansion valve lowers pressure of the liquid refrigerant, allowing the refrigerant to change phase from liquid to gas in the evaporator coil and draw required heat energy from air flowing overcoil 84 due to the air handler fan, to thereby cool air in the conditioned space. Also as discussed above, positive and negative pressure contributed bycompressor 76 in the refrigerant tubing line is sufficient so that the now-gaseous refrigerant flows back tocompressor 76 overtubing line 82 through reversingvalve 90, which fluidly connectsinput tubing line 82 to a compressorinput tubing line 95. - Referring to
FIG. 5 , when a temperature sensor (not shown) ofwater heater 68 sends an output signal toelectronic control system 70 indicating that the water temperature of water intank 68 has reached or fallen below the water heater's low set point temperature (as stored in memory at electronic control system 70), and if the COP comparison favors the refrigerant heat exchanger, the control system repositions waterheater regulator valve 104 and normallyopen solenoid valve 106 such that the refrigerant flows throughheat exchanger 88 and back intotubing portion 80, thereby adding refrigerant heat to the tank water, toexpansion valve 110. The settings ofvalves valves FIG. 2 . In addition,valves valve 98 remains closed. Refrigerant flowing throughcoil 84 changes phase to a gas, as discussed above with respect toFIG. 4 , and gaseous refrigerant returns tocompressor 76 viatubing - Although not shown in
FIG. 5 ,fan 74 is controlled by a variable fan speed controller (seeFIG. 2 ) that is, in turn, responsive to a pre-programmed target temperature in water-heating mode to control the speed offan 74 so that the refrigerant flowing fromcoil 72 andbypass valve 92 maintain the desired target temperature intubing 80, as described above with regard to the embodiment ofFIGS. 1 and 2 . The target temperature maybe selected as discussed above. - Similarly to operation of the embodiment discussed above with regard to
FIGS. 1 and 2 ,control system 70 may select the water heating source based on the COP comparison (data sets exist for the air conditioning modes of this embodiment) or may default to selection of the refrigerant heat exchanger to heat the water heater when the control system receives a temperature signal from the water heater indicating a need to heat water. Regardless of the method or of the heat source chosen, the control system thereafter continuously re-assesses the COP comparison and selects between the two alternative water heating sources based thereon, as described above. - It should be understood that the control system may change the system's operation modes between air cooling of the conditioned space and air heating of the conditioned space (or actuation from one mode to the other from start up), or to the inactive mode, based on operator control of the system or automatically. When the control system enters an air heating mode, and referring now
FIG. 6 , the control systemchanges reversing valve 90 so that the refrigerant flowing from the compressor throughtubing 91 flows throughvalve 90 totubing 82 that connects toindoor coil 84.Valve 98 remains closed.Coil 84, receiving the hot gaseous refrigerant fromcompressor 76, now acts as condenser, cooling the refrigerant so that it changes phase back to a liquid. Exitingcoil 84, the liquid refrigerant bypassesexpansion valve 110 through its internal check valve and flows through now-open solenoid valve 100 aroundcheck valve 109.Control system 70 maintainsvalve 106 open andvalves check valve 111 andclosed valve 108 otherwise block the refrigerant's flow intoheat exchanger 88, refrigerant fromcoil 84 flows throughvalve 106 and throughtubing 80 tooutdoor unit 64. The control system maintainsvalve 92 closed. Thus, all refrigerant from the indoor unit flows throughexpansion valve 94 and intooutdoor coil 72. Expansion valve 94 (which is bypassed by itsinternal check valve 93 when the system operates in air cooling modes) lowers the refrigerant's pressure, causingcoil 72 to act as an evaporator that draws heat from air passing over the coil as a result of operation offan 74. The now-warmer refrigerant flows fromcoil 72 toexpansion valve 90, which directs the refrigerant flow to the compressor'sinput tubing line 95. - Referring now to
FIG. 7 , if theelectronic control system 70 receives a signal from the temperature sensor atwater tank 86 indicating that the tank's water temperature has reached or fallen below the water heater's low set point whilesystem 60 is operating in an air heating mode,control system 70 decides whether to activate the heat exchanger or the water heater heat source, e.g., based on the data sets/COP comparison as described above, or by default to the heat exchanger followed by the data sets/COP comparison. Assuming the control system initially activates the heat exchanger, the control system appropriately adjustsvalves water heater 68 flows through coiledtubing heat exchanger 88. More specifically,control system 70 closesvalve 106 andvalve 92 and opensvalves - As discussed above,
indoor unit 66 includes an air handling unit having a fan that draws air overcoil 84. As indicated inFIG. 7 ,unit 66 also includes a variable speedfan control unit 115 in communication withcontrol system 70 and atemperature sensor 117 that detects refrigerant temperature in the flow of refrigerant combined from the output ofcoil 84 andbypass valve 98. As in the air cooling/water heating mode, when the system is in air heating/water heating mode,heat exchanger coil 88 acts as a sub-cooling or sub-condensing coil, sharing the condensing function with the system condenser, the difference between the two modes of operation being that in air heating mode,coil 84, rather thancoil 72, is the system condenser. As in the air cooling/water heating mode, the system in air heating/water heating mode diverts some of the hot gaseous refrigerant fromcompressor 76 tocoil 88, bypassing the condensing coil, in order to contribute heat to the heat exchanger. And as in the air cooling mode, this is accomplished in the air heating mode by a valve that bypasses the condenser coil, in thisinstance valve 98. That is,valve 98 serves the function in air heating/water heating mode thatvalve 92 serves in air cooling/water heating mode. - As discussed above with regard to
valve 92 in the air cooling/water heating mode, the opening ofvalve 98 in air heating/water heating mode allows hot gaseous refrigerant to flow through the bypass path, but because refrigerant flowing throughcondenser coil 84 is cooled, and thus has lower flow resistance than the hot refrigerant, more refrigerant tends to flow through the condenser coil than through the bypass when the air handler fan is operating at its normal speed. Accordingly, whencontrol system 70 actuatessystem 60 to operate in air heating/water heating mode, the control system instructs variablefan speed controller 115 to variably control the air handler fan speed in response to temperature of the combined refrigerant flow detected at 117 to maintain the refrigerant flow at 117 at a target temperature that is pre-programmed tocontroller 115 and/orcontrol system 70. The target temperature in air-heating mode may be selected independently of the air-cooling mode target temperature, as system conditions can be different. Thus, while the system actuatesrefrigerant heat exchanger 88, the air handler fan generally slows in speed, thereby increasing resistance to refrigerant flow through the condenser coil and forcing more refrigerant throughbypass valve 98. The bypass refrigerant remains in a hot, gaseous state so that the combination of gaseous refrigerant fromvalve 98 and liquid refrigerant fromcoil 84 is in a dual-phase state as it flows toheat exchanger 88. - This refrigerant flows through
open valve 108, aroundcheck valve 111, and throughheat exchanger coil 88. This transfers heat from the refrigerant to the water tank and completes the condensing process, so that therefrigerant leaving coil 88 throughopen valve 104 is in a fully liquid state. The liquid refrigerant continues its flow throughtubing 80 andvalve 94, aroundcheck valve 93, to expansion valve 113 andevaporator coil 72. From the evaporator coil, warmer, gaseous refrigerant flows throughtubing 80, reversingvalve 90, andinput tubing 95 tocompressor 76, and the cycle repeats. -
Control system 70 makes the COP comparison as described above to determine when to alternatively operaterefrigerant heat exchanger 88 or the water heater heat source. As when the system is operating in air cooling mode, the use ofrefrigerant heat exchanger 88 in air heating mode will generally be more efficient when the water intank 86 is at a lower temperature. Thus, whencontrol system 70 receives a signal from the water heater temperature sensor that the water heater is at or below its low set point temperature,control system 70 may default to operation ofrefrigerant heat exchanger 88 and thereafter continuously examines the efficiency comparison to determine when to switch to the water heater's operation. Again, since the target temperature to which fan controller 17 controls the refrigerant input to the heat exchanger is typically below the water heater's high set point temperature, this typically means that the refrigerant flow heat exchanger acts as a pre-heater and that final heating is effected by the water heater heat source. - It should also be recognized, in view of the present disclosure, that the reduction in the air handler fan speed during operation of
refrigerant heat exchanger 88 corresponds to a reduction of heat provided to the conditioned space, thereby corresponding to a reduction in system efficiency. When the system operates in air cooling/water heating mode, the system does not experience a similar efficiency reduction, in that because conditioned air is delivered to the conditioned space from the evaporator coil rather than from the condenser coil, energy contribution to the conditioned air is relatively unaffected by the refrigerant bypass around the condenser. As apparent from the discussion above,control system 70 may therefore switch from use ofheat exchanger 88 to the use of the water heater's heat source earlier in air heating/water heating mode than in air cooling/water heating mode. - In a still further embodiment, variable
speed fan controller 115 andsensor 117 may be omitted from the system, and the air handler fan may operate at normal speed during actuation ofheat exchanger 88 in air heating mode. This avoids the reduction in system efficiency caused by decrease in fan speed, although because of the resulting reduction in diversion of hot refrigerant to the heat exchanger throughvalve 98, the heat exchanger would correspondingly contribute less heat to the water heater, thereby reducing system efficiency. It will therefore be appreciated that the decision whether to utilize variable fan speed, and if so, also the selection of the target refrigerant temperature at the output of the bypass valve and the condenser coil, will influence system efficiency and, therefore, the balance between use ofrefrigerant heat exchanger 88 and the water heater heat source. It will also be understood that, in both air heating and air conditioning modes, decisions regarding use of fan reduction can be made, and operating parameter values optimized, through calibration of the particular air conditioning system. - In the discussion of the above-described embodiments, the control system actuates the refrigerant heat exchanger when the air conditioning system is operating either in an air cooling mode or an air heating mode. In certain embodiments, the control system only actuates the heat exchanger during an active mode of the air conditioning system, but in other embodiments the control system also actuates the refrigerant heat exchanger when the system is in an inactive mode, i.e. when running neither in air cooling mode nor air heating mode. In such embodiments, and referring for example to the system of
FIGS. 4-7 , ifcontrol system 70 receives a signal from the water heater temperature sensor indicating that water in the water heater has reached or fallen below the heater's low temperature set point, the control system decides whether to activate the heat exchanger or the water heater heat source, e.g., based on the COP comparison as described above, or by default to the heat exchanger. Assuming the decision is to activate the heat exchanger, the control system arranges the valves in the air conditioning system so as to operate in air heating/water heating mode, as discussed above with respect toFIG. 7 , and operates the air conditioning system in the manner described above with regard toFIG. 7 , except that the control system deactivates the air handler fan so that no air is drawn acrosscoil 84 and no conditioned air is provided to the conditioned space. Correspondingly, the variable fan speed controller is inoperative. This tends to force a greater volume of hot refrigerant from the compressor throughbypass valve 98, but the refrigerant flow is thereafter the same as discussed above with regard toFIG. 7 . The control system does operatefan 24, since the evaporator function is needed to complete the refrigerant cycle. Since the evaporator function is needed, the control system does not select an air cooling set up, as such arrangement would cause conditioned air to be forced into the conditioned space. - In this water heating-only mode of operation, the reduced condenser capacity causes the air conditioning system to remove less heat from the refrigerant between the compressor and the evaporator than in the air conditioning modes. The increased refrigerant heat corresponds to increased flow resistance in the refrigerant circuit and, therefore, to increased compressor discharge pressure. Depending on the system configuration, this may, in turn, so decrease system efficiency or possibly inhibit the compressor's operation that use of the refrigerant flow heat exchanger does not occur or occurs for only a short time. Thus, in embodiments utilizing a water heating-only mode,
compressor 76 may be a variable speed compressor so thatcontrol system 70 may reduce compressor speed when heating water with the heat exchanger but not conditioning air. For example, typical residential air conditioning systems have compressors ranging in capacity from 16,000 to 60,000 BTU/hr. In a non-air conditioning mode with water heating, however,control system 70 would lower a variable speed compressor to operate at a lower capacity, e.g. approximately 10,000 BTU/hr in a typical residential configuration. As in the air conditioning/water heating operational modes discussed above,control system 70 in a water heating-only mode again determines whether and when to switch between heating water with the refrigerant heat exchanger and heating water with the water heater heat source based on the COP comparison. - In the embodiments described above, the refrigerant heat exchanger coil is disposed downstream of the system condenser. In the embodiments discussed below with respect to
FIGS. 8-13 , however, the heat exchanger coil is disposed upstream from the system condenser, between the system condenser and the compressor. In these embodiments, the heat exchanger coil reduces heat of the hot gaseous refrigerant output by the compressor (and transfers this heat to the water heater), but it does not condense the refrigerant to a liquid phase. Because the heat exchanger coil receives hot refrigerant directly from the compressor, it is unnecessary to bypass the compressor output around the condenser or, therefore, to reduce condenser fan speed in order to encourage such bypass flow. That is, the system condenser fan operates at normal speed whether or not the refrigerant heat exchanger is active. This tends to increase system efficiency as compared to the embodiments described above with regard toFIGS. 1-7 . In certain environments, however, the embodiments described with regard toFIGS. 1-7 may be more convenient to install, particularly into an existing air conditioning system as a retrofit. -
FIG. 8 schematically depicts an air conditioning/water heater system 110 embodying principles of an embodiment of the present invention.System 110 includes (1) anair conditioning system 112 having anoutdoor coil unit 114 and anindoor coil unit 116, and (2) and associatedwater heater 118 which, representatively, may be a gas-fired or electric water heater. InFIG. 8 ,air conditioning system 112 is arranged so that it may operate alternatively in air heating and air cooling modes, and may therefore also be described as a heat pump. The various functions of the air conditioning/water heater system 110 are controlled by a schematically depicted electronic control circuit 120 (shown only inFIG. 8 ) that operates various subsequently described components ofoverall system 110. -
Outdoor unit 114 includes anoutdoor coil 122 and associatedfan 137 and acompressor 126.Condenser coil 122 andcompressor 126 are coupled, as shown, by a refrigerant tubing circuit having aline portion 130 betweencoil 122 and a reversingvalve 140 through anindoor unit coil 134 andexpansion valve 160, aline portion 131 between reversingvalve 140 andcompressor 126 via a heat conductive copper tube that is spiral-wrapped around ametal tank portion 136 ofwater heater 118 and serving as a refrigerant-to-tankwater heat exchanger 138 forwater heater 118, and aline portion 132 between reversingvalve 140 and each ofcoil 122 andcompressor 126. - In addition to reversing valve 190,
outdoor unit 114 includes an electronically controlledregulator valve 142, an expansion valve 153 at an input to outdoor coil 122 (bypassed when receiving outflow from coil 122),solenoid valves check valve 161.Valves electronic control system 120, which controls the actuation of these valves as discussed herein. - Turning now to
FIG. 9 , with the air conditioning/water heater system 110 in an air cooling only mode, electronic control system 120 (FIG. 8 ) setsvalves compressor 126 causes refrigerant discharged therefrom to flow, viatubing portion 131, to the entry point of a tubing loop that includesheat exchanger 138 wrapped aroundtank 136 ofwater heater 118.Electronic control system 120 has closedvalve 154 and openedvalve 144, so that hot gaseous refrigerant flowing fromcompressor 126 bypassesheat exchanger 138 and flows directly to reversingvalve 140.Control system 120 has set reversingvalve 140 so that the reversing valve directs this refrigerant flow, viatubing line 132, tooutdoor coil 122, which condenses the refrigerant in cooperation withfan 137 as discussed above. The refrigerant exitscoil 122 via tubing line 130 (bypassing expansion valve 163) and entersindoor coil 134 viaexpansion valve 160. As discussed above, and as should be understood,expansion valve 160 lowers the pressure of the refrigerant incoil 134 so thatcoil 134 functions as an evaporator. Anair handler fan 135adjacent coil 134 causes air to flow overcoil 134 and into the conditioned space. As discussed above, the refrigerant's change of phase in the evaporator coil from liquid to gas draws heat energy from this air, thereby causing the re-circulating air to cool the conditioned space. The now gaseous and warmer refrigerant flows fromcoil 134 viatubing portion 130 to reversingvalve 140, which directs the gaseous refrigerant flow, viatubing portion 132, back tocompressor 126, and the cycle repeats. - Referring to
FIG. 11 , when the system is operating in air cooling mode as described above with regard toFIG. 9 , and when a temperature sensor (not shown) ofwater heater 118 outputs a signal toelectronic control system 120 indicating to the electronic control system that the water heater water has reached or fallen below the water heater's low set point temperature as stored in the electronic control system, the control system decides whether to activate the heat exchanger or the water heater heat source, e.g., based on the COP comparison as described above or by default to the heat exchanger. Assuming the decision is to activate the heat exchanger, the electronic control system closesvalve 144 and opensvalve 154, thereby activatingrefrigerant heat exchanger 138. Reversingvalve 140 remains in the same setting as discussed with regard toFIG. 9 . Under these conditions, hot gaseous refrigerant output fromcompressor 126 flows toheat exchanger 138 ofwater heater 118 viatubing portion 131, bypassingvalve 144, and ultimately to reversingvalve 140 viacheck valve 161. The refrigerant flows from the reversing valve tooutdoor condenser coil 122, and then toexpansion valve 160,indoor coil 134, reversingvalve 140, and back tocompressor 126, as discussed above with respect toFIG. 9 . - Once the electronic control system actuates use of
heat exchanger 138 or the water heater heat source, the control system continuously assesses the data sets/COP comparison. If the resulting ratio drops below 1.0, the control system deactivates initially selected heat source and activates the other heat source. As noted above, system 110 (withheat exchanger 138 active) is generally more efficient than the system described above with respect toFIG. 2 orFIG. 5 , in that reduction of fan speed forcondenser coil 122 is unnecessary in air conditioning/water heating mode. Counterbalancing that positive efficiency effect is the longerrefrigerant tubing line 131 needed between the compressor and the water heater, but this effect is often offset and even overcome by the increase in efficiency caused by the cooling effect the refrigerant experiences as it travels throughheat exchanger 138. Accordingly, in most instances, operation of the system illustrated inFIG. 11 results in a positive system efficiency ratio, as compared to operation of the system and water heater heat source independently of each other, for a longer rise in temperature of water inwater heater tank 136 than does the systems described above with regard toFIG. 2 andFIG. 5 . In addition, since the water heater receives hot gaseous refrigerant directly fromcompressor 126, without need to regulate the refrigerant temperature being directed to the heat exchanger to a lower target temperature, as described above with regard toFIGS. 2 and 5 , the heat exchanger illustrated inFIG. 11 can transfer more heat to the water heater, thereby maintaining a positive contribution to system efficiency over a longer temperature range. Nonetheless, as long as the temperature of refrigerant flowing from the compressor toheat exchanger 138 is below the water heater's high temperature set point, the efficiency comparison will eventually favor operation of the water heater's heat source, causing the system to deactivate waterheater heat exchanger 138 and activate the water heater's inherent heat source. That is, under such circumstances, the water heater heat source will always bring the water heater water to the final high set point, andheat exchanger 138 serves as a pre-heater. Again, however, if the temperature of gaseous refrigerant fromcompressor 126 is at or higher than the water heater high set point, it is possible thatheat exchanger 138 can be used to bring the water heater fully to its high set point. -
Electronic control system 120 monitors pressure at the output ofcompressor 12 and, if the monitored pressure exceeds a predetermined pressure (provided by the compressor manufacturer or by user selection, for example after a calibration process),control system 120 may switchvalve 142 from a closed to an opened state, allowing refrigerant flow through atubing portion 145, bypassingheat exchanger 138 andcondenser coil 122, to the lower pressure of the evaporator. In one embodiment, and depending on the compressor capacity,control system 120 may selectively openproportional valve 142 whenever the compressor output pressure reaches or exceeds 550 psi. As will be understood in the context of the present disclosure, this reduces system efficiency, in that it diverts heat from transfer to the water heater and reduces the evaporator efficiency, and accordinglyvalve 142 is metered to minimize its impact. - If
control system 120 changes, either by manual or electronic control, from air cooling to air heating modes, without water heating and with reference toFIG. 10 ,control system 120 closesvalve 154, opensvalve 144, and sets reversingvalve 140 to direct refrigerant flow fromtubing line 131 toindoor coil 134 viatubing line 130 and to direct refrigerant flow fromcoil 122 vialine 132 back tocompressor 126 viatubing line 132. In operation, hot gaseous refrigerant flows fromcompressor 126 throughtubing line 131 andopen valve 144, bypassingheat exchanger 138 due toclosed valve 154. Reversingvalve 140 directs the gaseous refrigerant toindoor coil 134 viatubing line 130.Coil 134 acts as a condenser coil, cooling and condensing the refrigerant to liquid phase asair handler fan 135 moves air over the coils and into the conditioned space. The re-circulating building air draws heat energy from the refrigerant as it condenses, thereby providing a heating effect to the conditioned space. Leavingcoil 134 through tubing line 130 (and bypassing expansion valve 160), the now-liquid refrigerant flows tocoil 122 throughexpansion valve 163. The expansion valve lowers the refrigerant's pressure, causingoutdoor coil 122 to act as an evaporator, in which the refrigerant changes phase to a gas and draws heat energy from outdoor ambient air drawn over the coils byoutdoor unit fan 137. The now-warm gaseous refrigerant flows fromcoil 122 to reversingvalve 140, which directs the refrigerant flow back tocompressor 126 viatubing line 132, and the cycle repeats. - Referring now to
FIG. 12 , whenelectronic control system 120 receives a signal from the water heater water temperature sensor (not shown) indicating that the water heater water temperature has fallen below the water heater's low set point, when the air conditioning system is in air heating mode as discussed above with regard toFIG. 10 ,control system 120 decides whether to activate the heat exchanger or the water heater heat source, e.g. based on the data sets/COP comparison as described above, or by default to the heat exchanger. Assuming the decision is to activate the heat exchanger, the control system closesvalve 144 and opensvalve 154, thereby activatingheat exchanger 138 by including the heat exchanger and its related portion oftubing section 131 in the refrigerant flow loop. As described above, this causes hot gaseous refrigerant to flow fromcompressor 126 to and throughheat exchanger coil 138 viatubing section 131 and thereafter to reversingvalve 140 viacheck valve 161. The refrigerant's flow from reversingvalve 140, toindoor coil 134,expansion valve 163,outdoor coil 122, reversingvalve 140, and back tocompressor 126 occurs as discussed above with regard toFIG. 10 . - Again, when
electronic control system 120 receives the signal from the water heater water temperature sensor indicating that water heating is needed, the electronic control system may initially activaterefrigerant heat exchanger 138 rather than the water heater's inherent heat source, when the air conditioning system is operating in either air heating mode or air cooling mode, by default or by the COP comparison.FIGS. 9 and 11 illustrate the transition from air cooling-only mode to air cooling/water heating mode, whileFIGS. 10 and 12 illustrate the transition from air heating-only mode to air heating/water heating mode. Continuing the discussion of the latter transition, once the electronic control system has actuated the refrigerant heat exchanger, the electronic control system thereafter continuously monitors the COP comparison of system efficiency with operation ofrefrigerant water heater 138, and without operation of the water heater's heat source, to system efficiency with refrigerantflow heat exchanger 138 deactivated and the water heater's inherent heat source activated. If this ratio drops below 1.0 as the system operates, the electronic control system deactivates refrigerant flow heat exchanger 138 (by closingvalve 154 an opening valve 144), and activates the water heater's inherent heat source. As in all of the examples described herein,electronic control system 120 continues to monitor the water temperature output signal, and if the ratio rises above 1.0 and persists for a predetermined time will switch back to activation of the refrigerant flow heat exchanger. When the water heater water temperature rises to the water heater's high set point, the water heater heat source may be deactivated by a control system on the water heater that is independent ofelectronic control system 120, or the heat source may be deactivated bycontrol system 120. As discussed above with regard to air cooling mode, the temperature of refrigerant flowing fromcompressor 126 is also a limiting factor, as compared to the water heater's high set point. If the compressor's output refrigerant temperature is below the water heater's high set point, refrigerantflow heat exchanger 138 is always a pre-heating device. If the compressor refrigerant output temperature is higher than the water heater high set point, it is possible for refrigerantflow heat exchanger 138 to bring the water heater fully to its high set point. - As will be apparent in view of the present disclosure, operation of refrigerant
flow heat exchanger 138 in an air heating/water heating mode, as described with regard toFIG. 12 , results in the removal of heat from the refrigerant flow atheat exchanger 138 that might otherwise be removed atcoil 134 for contribution to conditioned air for the conditioned space. This may result in a reduced system efficiency as compared to the operation of the system in an air cooling/water heating mode, thereby resulting in a shorter duration of operation of the refrigerant heat exchanger in air heating/water heating mode than in a air cooling/water heating mode. -
Valve 142 is operated bycontrol system 120 in this mode in the same manner as discussed above with respect toFIGS. 9 and 11 . - Referring to
FIG. 13 ,electronic control system 120 receives a signal from the water heater water temperature sensor indicating that water heating is needed, whensystem 110 is in neither an air heating mode nor an air cooling mode,control system 120sets valves FIG. 12 , but does not activateair handler fan 135 because there is no call from the indoor thermostat to provide conditioned air to the conditioned space. Refrigerant flows through the refrigerant loop as described with regard toFIG. 12 . - Again, because
refrigerant heat exchanger 138 receives hot refrigerant gas directly fromcompressor 126, the system's ability to contribute heat to the water heater remains high in this mode of operation. However, the deactivation ofair handler fan 135 eliminates the corresponding air flow overcondenser coil 134, thereby reducing the system's ability to remove heat from the circulating refrigerant flow. This may undesirably increase pressure at the output ofcompressor 126. Wherecompressor 126 is a variable speed compressor, the control system changes the compressor's output to a lower level, e.g. 10,000 BTU/hr. Alternatively,electronic control system 120 opensbypass valve 142. This causes hot refrigerant gas fromcompressor 126 to bypassheat exchanger 138 andcoil 134 and flow directly tocoil 122 for return tocompressor 126. As described above, the opening ofbypass valve 142 may further decrease system efficiency, thereby increasing the likelihood of a switch to water heater activation. - It should be understood that the present system may be operated in various manners. For example, as discussed above, each of the embodiments described with regard to
FIGS. 1-13 can be operated based on a comparison of system efficiency when using the refrigerant heat exchanger to system efficiency when using the water heater's heat source, and relying on that comparison as the deciding factor whether to utilize the heat exchanger throughout the water heater's heat cycle. Rather than relying on the efficiency comparison, however, in a further embodiment the electronic control system, upon receiving a signal from the water heater temperature sensor indicating a need to heat water, actuates the refrigerant heat exchanger coil and maintains the heat exchanger coil active until the temperature signal reaches a predetermined point. This predetermined cut-off point may be determined through testing and comparison of system efficiencies alternatively utilizing the refrigerant flow heat exchanger and the water heater heat source. That is, the systems are operated under each of the alternative arrangements, and under similar operating conditions. System efficiencies are compared, and a temperature cut off is selected based on the comparison. Furthermore, temperature may be measured at various points in the water heater, as should be understood in the art, and in certain embodiments the electronic control system responds to water temperature taken at the lower portion of the lower tank. - Still further, in optional constructions of the air conditioning and water heating systems described above, the electronically controlled regulator valves may be replaced with fixed orifice solenoid valves, and the flow of hot refrigerant to the water heater refrigerant-to-water heat exchanger coils may instead be regulated by compressor discharge (head) pressure using an outdoor or indoor fan speed controller which is, in turn, controlled by the sensed water temperature in the water heater tank.
- Modifications and variations to the particular embodiments of the present invention may be practiced by those of ordinary skill in the art, without departing from the spirit and scope of the present invention, which is more particularly set forth in the appended claims. In addition, it should be understood that aspects of the various embodiments may be interchanged to both in whole or in part. Furthermore, those of ordinary skill in the art will appreciate that the foregoing description is by way of example only and is not intended to limit the invention so further described in the appended claims.
Claims (23)
1. Apparatus for heating water, comprising:
a tank for storing water;
a heat exchanger in thermal communication with the tank and configured to receive refrigerant and transfer heat therefrom to the tank;
an air conditioning system comprising
an air handler actuatable to move an air flow through an air flow path into a conditioned space,
a refrigerant path having a first portion that passes through the air flow path and a second portion that passes through the heat exchanger, and
a pump disposed in the refrigerant path and being actuatable to move refrigerant through the refrigerant path; and
a control system in operative communication with the air handler to control actuation of the air handler and in operative communication with the pump to control actuation of the pump,
wherein,
in a first mode of operation, the control system actuates the air handler to move the air flow through the air flow path and actuates the pump to move refrigerant through the first portion of the refrigerant path and the second portion of the refrigerant path, and
in a second mode of operation, the control system maintains the air handler in an inactive state and actuates the pump to move refrigerant through the first portion of the refrigerant path and the second portion of the refrigerant path.
2. The apparatus as in claim 1 , wherein the air conditioning system includes a thermostat operable to measure ambient temperature in the conditioned space and in communication with the control system to send a first signal to the control system corresponding to ambient temperature in the conditioned space, and wherein the control system selects operation in the first mode or the second mode in response to the first signal.
3. The apparatus as in claim 1 , wherein the air conditioning system includes a valve system within the refrigerant path that controls refrigerant flow to the first portion and the second portion and that is selectively configurable to alternatively allow refrigerant flow through the second portion and bypass refrigerant flow across the second portion.
4. The apparatus as in claim 3 , wherein the control system is in operative communication with the valve system to selectively configure the valve system to allow refrigerant flow through the second portion or bypass refrigerant flow across the second portion.
5. The apparatus as in claim 3 , wherein the air conditioning system includes a temperature sensor in thermal communication with water in the tank and in communication with the control system to send a second signal to the control system corresponding to temperature of the water, and wherein the control system is configured to control the valve system to allow refrigerant flow through the second portion or bypass refrigerant flow across the second portion, in response to the second signal.
6. The apparatus as in claim 3 , wherein the refrigerant path includes a first coil disposed in the air flow path and a second coil.
7. The apparatus as in claim 6 , wherein the air conditioning system includes a fan proximate the second coil so that operation of the fan moves an air flow across the second coil.
8. The apparatus as in claim 6 ,
wherein the valve system is selectively configurable between a first state and a second state,
wherein the refrigerant path is configured so that
in the first state, the refrigerant path flows from the pump, to the first coil, to the heat exchanger, to the second coil, and to the pump,
in the second state, the refrigerant path flows from the pump, to the second coil, to the heat exchanger, to the first coil, and to the pump, and
wherein the control system is in communication with the valve system to selectively move the valve system from one of the first state and the second state to the other of the first state and the second state.
9. The apparatus as in claim 8 , wherein the refrigerant path includes a first bypass path fluidly across the first coil and a second bypass path fluidly across the second coil.
10. The apparatus as in claim 9 , wherein
the valve system includes a first valve in the first bypass path that is selectively configurable to alternatively block and allow refrigerant flow through the first bypass path,
the valve system includes a second valve in the second bypass path that is selectively configurable to alternatively block and allow refrigerant flow through the second bypass path, and
the control system is in operative communication with the first valve and the second valve to respectively control the first and second valves to allow or block refrigerant fluid flow in the valves' respective bypass paths.
11. The apparatus as in claim 10 , wherein the control system is configured to configure the first valve to allow refrigerant flow through the first bypass path when the refrigerant path is configured to the first state, and wherein the control system is configured to configure the second valve to allow refrigerant flow through the second bypass path when the refrigerant path is configured to the second state.
12. The apparatus as in claim 6 ,
wherein the valve system is selectively configurable between a first state and a second state,
wherein the refrigerant path is configured so that
in the first state, the refrigerant path flows from the pump, to the heat exchanger, to the first coil, to the second coil, and to the pump,
in the second state, the refrigerant path flows from the pump, to the heat exchanger, to the second coil, to the first coil, and to the pump, and
wherein the control system is in communication with the valve system to selectively move the valve system from one of the first state and the second state to the other of the first state and the second state.
13. The apparatus as in claim 3 , wherein in a third mode of operation, the control system actuates the air handler to move the air flow through the air flow path, actuates the pump to move refrigerant through the first portion of the refrigerant path and sets the valve system to bypass refrigerant flow across the second portion.
14. Apparatus for heating water, comprising:
a tank for storing water and including a temperature sensor in thermal communication with water in the tank and configured to output a first signal corresponding to temperature of the water;
a heat exchanger in thermal communication with the tank and configured to receive refrigerant and transfer heat therefrom to the tank; and
an air conditioning system comprising
an air handler actuatable to move an air flow through an air flow path into a conditioned space,
a refrigerant path having a first portion that passes through the air flow path and a second portion that passes through the heat exchanger,
a valve system within the refrigerant path that controls refrigerant flow to the first portion and the second portion and that is selectively configurable to alternatively allow refrigerant flow through the second portion and block refrigerant flow through the second portion
a pump disposed in the refrigerant path and being actuatable to move refrigerant through the refrigerant path, and
a thermostat operable to measure ambient temperature in the conditioned space and to output a second signal corresponding to ambient temperature in the conditioned space, and
a control system in operative communication with the tank to receive the first signal, in operative communication with the air handler to control actuation of the air handler, in operative communication with the pump to control actuation of the pump, in operative communication with the valve system to selectively allow refrigerant flow through the second portion and block refrigerant flow through the second portion, and in operative communication with the thermostat to receive the second signal,
wherein, in response to the first signal and the second signal,
in a first mode of operation, the control system actuates the air handler to move the air flow through the air flow path, actuates the pump to move refrigerant through the refrigerant path, and configures the valve system to allow refrigerant flow through the second portion,
in a second mode of operation, the control system maintains the air handler in an inactive state, actuates the pump to move refrigerant through the refrigerant path, and configures the valve system to allow refrigerant flow through the second portion, and
in a third mode of operation, the control system actuates the air handler to move the air flow through the air flow path, actuates the pump to move refrigerant through the refrigerant path, and configures the valve system to block refrigerant flow through the second portion.
15. An apparatus for heating water, comprising:
a tank for storing water and having a heat source;
a heat exchanger in thermal communication with the tank and configured to receive refrigerant and transfer heat therefrom to the tank;
an air conditioning system comprising
an air handler actuatable to move an air flow through an air flow path into a conditioned space,
a refrigerant path having a first portion that passes through the air flow path and a second portion that passes through the heat exchanger, and
a pump disposed in the refrigerant path and being actuatable to move refrigerant through the refrigerant path;
a plurality of sensors, each outputting a respective signal representative of a respective system operating parameter; and
a control system in operative communication with the tank to control operation of the heat source, in operative communication with the air handler to control actuation of the air handler, in operative communication with the sensors to receive the respective signals, and in operative communication with the refrigerant path to control refrigerant flow, and
wherein, in response to the signals from the sensors, the control system selectively allows or blocks refrigerant flow through the second portion and selectively actuates the water heater heat source.
16. An apparatus for heating water, comprising:
a tank for storing water and having a heat source;
a heat exchanger in thermal communication with the tank and configured to receive refrigerant and transfer heat therefrom to the tank;
an air conditioning system comprising
an air handler actuatable to move an air flow through an air flow path into a conditioned space,
a refrigerant path having a first portion that passes through the air flow path and a second portion that passes through the heat exchanger,
a pump disposed in the refrigerant path and being actuatable to move refrigerant through the refrigerant path, and
a valve system within the refrigerant path that controls refrigerant flow in the first portion and the second portion and that is selectively configurable to alternatively allow refrigerant flow through the second portion and block refrigerant flow in the second portion;
a plurality of sensors, each outputting a respective signal representative of a respective system operating parameter that varies in a predetermined relationship with operating efficiency of at least one of the tank and the air conditioning system; and
a control system in operative communication with the tank to control operation of the heat source, in operative communication with the air handler to control actuation of the air handler, in operative communication with the sensors to receive the respective signals, and in operative communication with valve system to control refrigerant flow, and
wherein, in response to the respective signals from the sensors, the control system selectively actuates the valve system to allow refrigerant flow through the second portion or block refrigerant flow through second portion and selectively actuates the water heater heat source.
17. The apparatus as in claim 16 , wherein the plurality of sensors comprises a thermostat that is operable to detect an air temperature of the conditioned space and output a signal to the control system that corresponds to the temperature.
18. The apparatus as in claim 16 , wherein the plurality of sensors comprises a temperature sensor in thermal communication with water in the tank and that is operable to output a signal to the control system that corresponds to a temperature of the water.
19. The apparatus as in claim 16 , wherein the plurality of sensors comprises a temperature sensor disposed proximate the refrigerant path and is operable to detect a temperature of ambient air proximate the refrigerant path and output a signal to the control system that corresponds to the temperature.
20. The apparatus as in claim 19 , wherein the refrigerant path comprises a first coil disposed within the air flow path and a second coil disposed exterior to the conditioned space, and wherein the temperature sensor is configured.
21. Apparatus for heating water, comprising:
a tank for storing water;
a heat exchanger in thermal communication with the tank and configured to receive refrigerant and transfer heat therefrom to the tank;
an air conditioning system operative to utilize refrigerant flowing through a refrigerant circuit portion of the air conditioning system to regulate temperature of air being delivered to a conditioned space, wherein the refrigerant circuit portion is in fluid communication with the heat exchanger so that refrigerant flowing through the refrigerant circuit portion flows through the heat exchanger; and
a control system in operative communication with the air conditioning system to control operation of the air conditioning system and temperature of the refrigerant delivered in the refrigerant circuit to the heat exchanger, wherein the control system controls the temperature of the refrigerant delivered to the heat exchanger to a predetermined target temperature.
22. Apparatus for heating water, comprising:
a tank for storing water;
a heat exchanger in thermal communication with the tank and configured to receive refrigerant and transfer heat therefrom to the tank;
an air conditioning system operative to utilize refrigerant flowing through a refrigerant circuit portion of the air conditioning system to regulate temperature of air being delivered to a conditioned space, wherein the refrigerant circuit portion is in fluid communication with the heat exchanger so that refrigerant flowing through the refrigerant circuit portion flows through the heat exchanger; and
a control system in operative communication with the air conditioning system to control operation of the air conditioning system, wherein
the control system is configured to selectively direct flow of the refrigerant in the refrigerant circuit portion to the heat exchanger and block flow of refrigerant in the refrigerant circuit portion from flowing through the heat exchanger,
the control system is configured, in a first mode of operation, to direct flow of the refrigerant in the refrigerant circuit portion to the heat exchanger when the air conditioning system is delivering conditioned air to the conditioned space, and
the control system is configured, in a second mode of operation, to direct flow of the refrigerant in the refrigerant circuit portion to the heat exchanger when the air conditioning system is not delivering conditioned air to the conditioned space.
23. Apparatus for heating water, comprising:
a tank for storing water and having a heat source;
a heat exchanger in thermal communication with the tank and configured to receive refrigerant and transfer heat therefrom to the tank;
an air conditioning system operative to utilize refrigerant flowing through a refrigerant circuit portion of the air conditioning system to regulate temperature of air being delivered to a conditioned space, wherein the refrigerant circuit portion is in fluid communication with the heat exchanger so that refrigerant flowing through the refrigerant circuit portion flows through the heat exchanger; and
a control system in operative communication with the air conditioning system to control operation of the air conditioning system and in operative communication with the tank to control operation of the heat source, wherein
the control system is configured to selectively direct flow of the refrigerant in the refrigerant circuit portion to the heat exchanger and block flow of refrigerant in the refrigerant circuit portion from flowing through the heat exchanger,
the control system is configured, in a first mode of operation, to direct flow of the refrigerant in the refrigerant circuit portion to the heat exchanger and deactivate the heat source,
the control system is configured, in a second mode of operation, to block flow of the refrigerant in the refrigerant circuit portion to the heat exchanger and activate the heat source, and
the control system is configured to select between the first mode of operation and the second mode of operation based on efficiency of the air conditioning system when the control system operates in the first mode and efficiency of the air conditioning system when the control system operates in the second mode.
Priority Applications (10)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
MX2015012402A MX2015012402A (en) | 2013-03-13 | 2014-03-13 | Apparatus and methods for heating water with refrigerant from air conditioning system. |
CN201480024058.8A CN105518397B (en) | 2013-03-13 | 2014-03-13 | Using the apparatus and method of the refrigerant heat water from air handling system |
US14/210,383 US9879881B2 (en) | 2013-03-13 | 2014-03-13 | Apparatus and methods for heating water with refrigerant from air conditioning system |
AU2014243719A AU2014243719B2 (en) | 2013-03-13 | 2014-03-13 | Apparatus and methods for heating water with refrigerant from air conditioning system |
CA2906662A CA2906662C (en) | 2013-03-13 | 2014-03-13 | Apparatus and methods for heating water with refrigerant from air conditioning system |
PCT/US2014/026894 WO2014160514A2 (en) | 2013-03-13 | 2014-03-13 | Apparatus and methods for heating water with refrigerant from air conditioning system |
CA3020438A CA3020438C (en) | 2013-03-13 | 2014-03-13 | Apparatus and methods for heating water with refrigerant from air conditioning system |
AU2017258806A AU2017258806B2 (en) | 2013-03-13 | 2017-11-06 | Apparatus and methods for heating water with refrigerant from air conditioning system |
US15/882,756 US10871307B2 (en) | 2013-03-13 | 2018-01-29 | Apparatus and methods for heating water with refrigerant from air conditioning system |
US17/128,393 US20210108829A1 (en) | 2013-03-13 | 2020-12-21 | Apparatus and methods for heating water with refrigerant from air conditioning system |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US201361779087P | 2013-03-13 | 2013-03-13 | |
US14/210,383 US9879881B2 (en) | 2013-03-13 | 2014-03-13 | Apparatus and methods for heating water with refrigerant from air conditioning system |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US15/882,756 Continuation US10871307B2 (en) | 2013-03-13 | 2018-01-29 | Apparatus and methods for heating water with refrigerant from air conditioning system |
Publications (2)
Publication Number | Publication Date |
---|---|
US20140260392A1 true US20140260392A1 (en) | 2014-09-18 |
US9879881B2 US9879881B2 (en) | 2018-01-30 |
Family
ID=51521097
Family Applications (5)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/189,192 Active 2034-07-18 US9389000B2 (en) | 2013-03-13 | 2014-02-25 | Apparatus and methods for pre-heating water with air conditioning unit or heat pump |
US14/210,383 Active 2034-09-24 US9879881B2 (en) | 2013-03-13 | 2014-03-13 | Apparatus and methods for heating water with refrigerant from air conditioning system |
US15/207,170 Active 2034-03-12 US9945582B2 (en) | 2013-03-13 | 2016-07-11 | Apparatus and methods for pre-heating water with air conditioning unit or heat pump |
US15/882,756 Active 2035-01-10 US10871307B2 (en) | 2013-03-13 | 2018-01-29 | Apparatus and methods for heating water with refrigerant from air conditioning system |
US17/128,393 Pending US20210108829A1 (en) | 2013-03-13 | 2020-12-21 | Apparatus and methods for heating water with refrigerant from air conditioning system |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/189,192 Active 2034-07-18 US9389000B2 (en) | 2013-03-13 | 2014-02-25 | Apparatus and methods for pre-heating water with air conditioning unit or heat pump |
Family Applications After (3)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US15/207,170 Active 2034-03-12 US9945582B2 (en) | 2013-03-13 | 2016-07-11 | Apparatus and methods for pre-heating water with air conditioning unit or heat pump |
US15/882,756 Active 2035-01-10 US10871307B2 (en) | 2013-03-13 | 2018-01-29 | Apparatus and methods for heating water with refrigerant from air conditioning system |
US17/128,393 Pending US20210108829A1 (en) | 2013-03-13 | 2020-12-21 | Apparatus and methods for heating water with refrigerant from air conditioning system |
Country Status (10)
Country | Link |
---|---|
US (5) | US9389000B2 (en) |
EP (3) | EP2972008B1 (en) |
CN (3) | CN105264305A (en) |
AU (4) | AU2014249864B2 (en) |
BR (1) | BR112015022343B1 (en) |
CA (3) | CA2905278C (en) |
CL (1) | CL2015002578A1 (en) |
DK (1) | DK2972008T3 (en) |
MX (2) | MX2015012306A (en) |
WO (2) | WO2014163898A1 (en) |
Cited By (31)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20150000324A1 (en) * | 2013-06-26 | 2015-01-01 | Gd Midea Heating & Ventilating Equipment Co., Ltd. | Water tank and heat pump water heater comprising the same |
US20150338108A1 (en) * | 2013-07-26 | 2015-11-26 | Eco Factory Co., Ltd. | Air conditioning system and operation method for air conditioning system |
WO2016036688A1 (en) * | 2014-09-02 | 2016-03-10 | Rheem Manufacturing Company | Apparatus and method for hybrid water heating and air cooling and control thereof |
WO2016094949A1 (en) * | 2014-12-17 | 2016-06-23 | HABCHI, Jason | A hide-away air-conditioning system |
US20170211824A1 (en) * | 2016-01-26 | 2017-07-27 | Lennox Industries Inc. | Heating furnace using anti-stratification mode |
US20170211820A1 (en) * | 2016-01-26 | 2017-07-27 | Lennox Industries Inc. | Heating furnace using energy saving mode |
US20170351277A1 (en) * | 2016-06-01 | 2017-12-07 | International Business Machines Corporation | Energy efficient hot water distribution |
US20180010822A1 (en) * | 2016-07-06 | 2018-01-11 | Rheem Manufacturing Company | Apparatus and methods for heating water with refrigerant and phase change material |
US20180010829A1 (en) * | 2016-07-08 | 2018-01-11 | Climate Master, Inc. | Heat pump and water heater |
US9879881B2 (en) | 2013-03-13 | 2018-01-30 | Rheem Manufacturing Company | Apparatus and methods for heating water with refrigerant from air conditioning system |
US20180347868A1 (en) * | 2016-02-08 | 2018-12-06 | Mitsubishi Electric Corporation | Air-conditioning apparatus |
US10345004B1 (en) | 2015-09-01 | 2019-07-09 | Climate Master, Inc. | Integrated heat pump and water heating circuit |
US10753661B2 (en) | 2014-09-26 | 2020-08-25 | Waterfurnace International, Inc. | Air conditioning system with vapor injection compressor |
US10794620B2 (en) * | 2016-09-12 | 2020-10-06 | Mitsubishi Electric Corporation | Air-conditioning apparatus |
US10866002B2 (en) | 2016-11-09 | 2020-12-15 | Climate Master, Inc. | Hybrid heat pump with improved dehumidification |
US10935260B2 (en) | 2017-12-12 | 2021-03-02 | Climate Master, Inc. | Heat pump with dehumidification |
CN113137676A (en) * | 2020-01-20 | 2021-07-20 | 兄弟工业株式会社 | Air conditioner |
US11067319B2 (en) | 2018-03-05 | 2021-07-20 | Johnson Controls Technology Company | Heat exchanger with multiple conduits and valve control system |
US11067296B2 (en) * | 2015-11-20 | 2021-07-20 | Sens Geoenergy Storage Ab | Heat pump system and method for controlling a heat pump system |
US11143420B2 (en) * | 2016-12-21 | 2021-10-12 | Mitsubishi Electric Corporation | Air-conditioning apparatus |
US11215388B2 (en) * | 2019-01-21 | 2022-01-04 | Carrier Corporation | Refrigerant charge management |
US20220010978A1 (en) * | 2020-07-13 | 2022-01-13 | Rheem Manufacturing Company | Integrated space conditioning and water heating/cooling systems and methods thereto |
US11293666B2 (en) * | 2017-11-07 | 2022-04-05 | Nanjing University Of Aeronautics And Astronautics | Superhigh temperature heat pump system and method capable of preparing boiling water not lower than 100° C |
WO2022103726A1 (en) * | 2020-11-10 | 2022-05-19 | Rheem Manufacturing Company | Air recirculation systems for heat pumps |
US20220341628A1 (en) * | 2021-04-26 | 2022-10-27 | Villara Corporation | Providing domestic hot water from conventional residential split system heat pumps |
US11506430B2 (en) | 2019-07-15 | 2022-11-22 | Climate Master, Inc. | Air conditioning system with capacity control and controlled hot water generation |
US11592215B2 (en) | 2018-08-29 | 2023-02-28 | Waterfurnace International, Inc. | Integrated demand water heating using a capacity modulated heat pump with desuperheater |
US11690145B2 (en) * | 2015-12-17 | 2023-06-27 | Convotherm-Elektrogerate Gmbh | Method for operating a commercial cooking device and such a cooking device |
US11719453B2 (en) | 2018-01-21 | 2023-08-08 | Daikin Industries, Ltd. | System and method for heating and cooling |
US11781760B2 (en) | 2020-09-23 | 2023-10-10 | Rheem Manufacturing Company | Integrated space conditioning and water heating systems and methods thereto |
US11859868B2 (en) * | 2017-10-30 | 2024-01-02 | Rheem Manufacturing Company | Hybrid water heater |
Families Citing this family (44)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20150060007A1 (en) * | 2012-04-13 | 2015-03-05 | Benson Global Pty Ltd. | Heat pump |
JP6384057B2 (en) * | 2014-02-03 | 2018-09-05 | ダイキン工業株式会社 | Air conditioning system |
PT3183506T (en) * | 2014-08-20 | 2021-01-05 | Intellihot Inc | Combined hot water and air heating and conditioning system including heat pump |
US9783024B2 (en) | 2015-03-09 | 2017-10-10 | Bergstrom Inc. | System and method for remotely managing climate control systems of a fleet of vehicles |
EP3067645A1 (en) * | 2015-03-12 | 2016-09-14 | Hiref S.p.A. | Optimized multi-purpose refigeration circuit |
KR101714900B1 (en) * | 2015-09-30 | 2017-03-09 | 엘지전자 주식회사 | A gas heat-pump system |
US10634394B2 (en) * | 2015-12-18 | 2020-04-28 | Samsung Electronics Co., Ltd. | Air conditioner outdoor unit including heat exchange apparatus |
US9874384B2 (en) | 2016-01-13 | 2018-01-23 | Bergstrom, Inc. | Refrigeration system with superheating, sub-cooling and refrigerant charge level control |
US10589598B2 (en) | 2016-03-09 | 2020-03-17 | Bergstrom, Inc. | Integrated condenser and compressor system |
SE540118C2 (en) * | 2016-06-16 | 2018-04-03 | Flaekt Woods Ab | Method and apparatus for reducing or eliminating the lowering of the supply air temperature during the defrosting of an evaporator by an air treatment unit |
US10081226B2 (en) | 2016-08-22 | 2018-09-25 | Bergstrom Inc. | Parallel compressors climate system |
US10562372B2 (en) | 2016-09-02 | 2020-02-18 | Bergstrom, Inc. | Systems and methods for starting-up a vehicular air-conditioning system |
ES2802229T3 (en) * | 2016-09-23 | 2021-01-18 | Daikin Ind Ltd | System for air conditioning and hot water supply |
EP3299735B1 (en) * | 2016-09-23 | 2022-11-23 | Daikin Industries, Limited | System for air-conditioning and hot-water supply |
EP3299734B1 (en) * | 2016-09-23 | 2024-03-06 | Daikin Industries, Ltd. | System for air-conditioning and hot-water supply |
EP3299738A1 (en) * | 2016-09-23 | 2018-03-28 | Daikin Industries, Limited | System for air-conditioning and hot-water supply |
US10675948B2 (en) | 2016-09-29 | 2020-06-09 | Bergstrom, Inc. | Systems and methods for controlling a vehicle HVAC system |
US10724772B2 (en) | 2016-09-30 | 2020-07-28 | Bergstrom, Inc. | Refrigerant liquid-gas separator having an integrated check valve |
US10323859B2 (en) * | 2016-10-27 | 2019-06-18 | King Fahd University Of Petroleum And Minerals | Water mixing system for thermoregulating water |
CN106546025A (en) * | 2016-12-07 | 2017-03-29 | 珠海格力电器股份有限公司 | Heat-exchange system and air-conditioner |
CN107062674A (en) * | 2017-01-13 | 2017-08-18 | 中山市爱美泰电器有限公司 | It is a kind of set within doors dehumidifying and domestic hot-water heat pump air conditioner |
FR3063132B1 (en) * | 2017-02-23 | 2019-06-07 | Atlantic Climatisation & Ventilation | THERMAL MANAGEMENT SYSTEM FOR AIR AND HOT WATER PRODUCTION FOR A LOCAL |
EP3586065A4 (en) | 2017-02-27 | 2021-06-02 | Zinniatek Limited | A system for conditioning air in a living space |
CN108981095A (en) * | 2017-06-01 | 2018-12-11 | 博世热力技术(山东)有限公司 | Heat pump unit control method, device and heat pump unit |
GB201709759D0 (en) * | 2017-06-19 | 2017-08-02 | Magic Thermodynamic Box Ltd | Water heating apparatus |
US11448441B2 (en) | 2017-07-27 | 2022-09-20 | Bergstrom, Inc. | Refrigerant system for cooling electronics |
JP6963939B2 (en) * | 2017-08-31 | 2021-11-10 | リンナイ株式会社 | Hot water supply system |
CN111279145B (en) | 2017-09-19 | 2022-05-27 | 埃科莱布美国股份有限公司 | Cooling water monitoring and control system |
CN107477867A (en) * | 2017-09-29 | 2017-12-15 | 合肥美的暖通设备有限公司 | Teat pump boiler and its control method |
FR3073274B1 (en) * | 2017-11-06 | 2019-10-25 | Emile Ivars Paul | DEVICE FOR PRODUCING HOT SANITARY WATER AND HEATING / REFRESHING |
PL3707457T3 (en) | 2017-11-10 | 2023-01-09 | Ecolab USA, Inc. | Cooling water monitoring and control method |
CN108167975A (en) * | 2017-12-07 | 2018-06-15 | 新奥泛能网络科技股份有限公司 | Heat pump cold-hot combined supply system |
CN108181101B8 (en) * | 2018-01-11 | 2020-04-07 | 新丰县建筑安装工程有限公司 | Building door and window shading performance detection device and control method thereof |
US11420496B2 (en) | 2018-04-02 | 2022-08-23 | Bergstrom, Inc. | Integrated vehicular system for conditioning air and heating water |
CN108758916A (en) * | 2018-06-28 | 2018-11-06 | 北京艾尔绿能科技有限公司 | A kind of double end air source heat pump heating air conditioning units of fluorine water |
CN108759152A (en) * | 2018-06-28 | 2018-11-06 | 北京艾尔绿能科技有限公司 | A kind of double end air source heat pump heating air conditioning units of perfluor |
CN109210820A (en) * | 2018-09-13 | 2019-01-15 | 珠海格力电器股份有限公司 | A kind of multifunctional heat pump and its switching method for implementing different function |
JP2020070999A (en) * | 2018-11-01 | 2020-05-07 | 株式会社長府製作所 | Air-conditioning hot water storage device |
US20200309394A1 (en) * | 2019-03-26 | 2020-10-01 | Johnson Controls Technology Company | Hvac unit utilizing selectively modulated flow rates with hot gas reheat circuit |
CN110207296B (en) * | 2019-06-12 | 2021-04-02 | 珠海格力电器股份有限公司 | Air-conditioning and water-heating dual-purpose system and heating control method thereof |
TWI730747B (en) * | 2020-05-04 | 2021-06-11 | 台灣櫻花股份有限公司 | Method for intelligently adjusting temperature of water heater |
US11768018B2 (en) * | 2021-05-03 | 2023-09-26 | Matthew Desmarais | Double hybrid heat pumps and systems and methods of use and operations |
US11686489B2 (en) * | 2021-06-10 | 2023-06-27 | Johnson Controls Technology Company | Modulating reheat functionality for HVAC system |
CN118019947A (en) * | 2021-07-23 | 2024-05-10 | 维里(Pty)有限公司 | Dual-function water heater and air conditioning unit |
Citations (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4449375A (en) * | 1982-03-29 | 1984-05-22 | Carrier Corporation | Method and apparatus for controlling the operation of an indoor fan associated with an air conditioning unit |
US5628200A (en) * | 1995-01-12 | 1997-05-13 | Wallace Heating & Air Conditioning, Inc. | Heat pump system with selective space cooling |
US6357245B1 (en) * | 2001-05-01 | 2002-03-19 | Cohand Technology Co., Ltd. | Apparatus for making hot-water by air conditioner/heater |
US20040144528A1 (en) * | 2002-02-12 | 2004-07-29 | Keijiro Kunimoto | Heat pump water heater |
US20050109490A1 (en) * | 2001-12-12 | 2005-05-26 | Steve Harmon | Energy efficient heat pump systems for water heating and airconditioning |
US20060042285A1 (en) * | 2004-09-01 | 2006-03-02 | Behr Gmbh & Co. Kg | Stationary vehicle air conditioning system |
US20060179874A1 (en) * | 2005-02-17 | 2006-08-17 | Eric Barger | Refrigerant based heat exchange system |
US20080245087A1 (en) * | 2007-04-07 | 2008-10-09 | John Walter Orcutt | System for controlled fluid heating using air conditioning waste heat |
US20090049857A1 (en) * | 2006-04-20 | 2009-02-26 | Carrier Corporation | Heat pump system having auxiliary water heating and heat exchanger bypass |
US20090248212A1 (en) * | 2008-03-25 | 2009-10-01 | Cowans Kenneth W | Thermal control system and method |
US20140230477A1 (en) * | 2011-09-30 | 2014-08-21 | Daikin Industries, Ltd. | Hot water supply air conditioning system |
Family Cites Families (89)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1874803A (en) * | 1931-01-12 | 1932-08-30 | Reed Frank Maynard | Heat exchange mechanism |
US2375157A (en) * | 1940-12-03 | 1945-05-01 | Wilkes Gilbert | Heat pump system |
US3308877A (en) * | 1965-07-01 | 1967-03-14 | Carrier Corp | Combination conditioning and water heating apparatus |
US4012920A (en) | 1976-02-18 | 1977-03-22 | Westinghouse Electric Corporation | Heating and cooling system with heat pump and storage |
US4238933A (en) | 1978-03-03 | 1980-12-16 | Murray Coombs | Energy conserving vapor compression air conditioning system |
SE424889B (en) | 1978-03-15 | 1982-08-16 | Sjostrand Nils Eric | CONDENSATE DRAINAGE DEVICE |
US4227382A (en) | 1978-10-04 | 1980-10-14 | General Electric Company | Split system air conditioner adapted to receive a water preheater |
US4215551A (en) * | 1978-10-12 | 1980-08-05 | Johnes John W | Environmentally assisted heating and cooling system |
US4293323A (en) * | 1979-08-30 | 1981-10-06 | Frederick Cohen | Waste heat energy recovery system |
NO793312L (en) * | 1979-10-15 | 1981-04-21 | Thorleif Moell | DEVICE FOR HEAT PUMPS. |
US4281519A (en) | 1979-10-25 | 1981-08-04 | Carrier Corporation | Refrigeration circuit heat reclaim method and apparatus |
US4356706A (en) * | 1980-08-05 | 1982-11-02 | Ronald Baumgarten | Thermally-integrated heat exchanger and refrigerator |
US4382368A (en) * | 1981-03-20 | 1983-05-10 | Dittell Edward W | Geothermal hot water system |
US4599870A (en) * | 1981-03-25 | 1986-07-15 | Hebert Theodore M | Thermosyphon heat recovery |
US4386500A (en) | 1981-04-01 | 1983-06-07 | Boyd Sigafoose | Water heater heat exchange apparatus, kit, and method of installation |
US4448347A (en) * | 1981-12-09 | 1984-05-15 | Dunstan Phillip E | Heat pump system using wastewater heat |
US4391104A (en) * | 1982-01-15 | 1983-07-05 | The Trane Company | Cascade heat pump for heating water and for cooling or heating a comfort zone |
US4452050A (en) * | 1983-03-14 | 1984-06-05 | Heat Transfer Engineering, Inc. | Energy efficient water heating device and system |
CA1214336A (en) | 1983-10-11 | 1986-11-25 | Sven G. Oskarsson | Heat pump system |
KR900000809B1 (en) | 1984-02-09 | 1990-02-17 | 미쓰비시전기 주식회사 | Room-warming/cooling and hot-water supplying heat-pump apparatus |
US4645908A (en) | 1984-07-27 | 1987-02-24 | Uhr Corporation | Residential heating, cooling and energy management system |
US4685307A (en) * | 1984-07-27 | 1987-08-11 | Uhr Corporation | Residential heating, cooling and energy management system |
US4693089A (en) | 1986-03-27 | 1987-09-15 | Phenix Heat Pump Systems, Inc. | Three function heat pump system |
JPH01208646A (en) * | 1988-02-15 | 1989-08-22 | Sanden Corp | Controller of cooling, heating and hot-water supply system |
SE464667B (en) * | 1988-08-22 | 1991-05-27 | Thermia Ab | HEAT PUMP INSTALLATION FOR HEATING OR COOLING THE SPACES AND HEATING OF THE TAPP HEAT WATER |
US5003788A (en) | 1989-09-05 | 1991-04-02 | Gas Research Institute | Gas engine driven heat pump system |
US5050394A (en) | 1990-09-20 | 1991-09-24 | Electric Power Research Institute, Inc. | Controllable variable speed heat pump for combined water heating and space cooling |
US5081846A (en) | 1990-09-21 | 1992-01-21 | Carrier Corporation | Control of space heating and water heating using variable speed heat pump |
US5105633A (en) | 1991-01-28 | 1992-04-21 | Venturedyne, Ltd. | Solvent recovery system with means for supplemental cooling |
US5269153A (en) | 1991-05-22 | 1993-12-14 | Artesian Building Systems, Inc. | Apparatus for controlling space heating and/or space cooling and water heating |
CA2128725A1 (en) * | 1992-11-25 | 1994-06-09 | Toshio Eki | Combinaiton faucet and method of mixing hot water with cold water |
JP3060770B2 (en) | 1993-02-26 | 2000-07-10 | ダイキン工業株式会社 | Refrigeration equipment |
US5495723A (en) | 1994-10-13 | 1996-03-05 | Macdonald; Kenneth | Convertible air conditioning unit usable as water heater |
US5575159A (en) | 1995-06-02 | 1996-11-19 | Dittell; Edward W. | Heat energy transfer system |
JP2761200B2 (en) | 1995-06-06 | 1998-06-04 | 富士インジェクタ株式会社 | High / low pressure path reversal switching device for air conditioner |
US5906104A (en) | 1997-09-30 | 1999-05-25 | Schwartz; Jay H. | Combination air conditioning system and water heater |
JPH11270920A (en) * | 1998-03-20 | 1999-10-05 | Mitsubishi Electric Corp | Multifunctional heat pump system and method of its operation control |
GB2339890A (en) * | 1998-07-17 | 2000-02-09 | Pichit Likitcheva | Heat recovery from refrigeration and air conditioning systems |
DE10058273A1 (en) * | 2000-11-23 | 2002-05-29 | Woelfle Gmbh | Ventilator comprises heat pump unit, service and drinking water accumulator, heating water accumulator, electric heater, heat exchanger, closeable connections. |
US6536221B2 (en) | 2001-01-16 | 2003-03-25 | Norbert L. James | Air conditioning heat recovery arrangement |
CN1177182C (en) * | 2001-05-12 | 2004-11-24 | 中国科学技术大学 | Energy-saving cold-heat air-conditioning, water-heating three-purpose machine capable of being used all gear round |
AUPR840901A0 (en) | 2001-10-22 | 2001-11-15 | Southcorp Australia Pty Ltd | Improvements in heat pump water heaters |
JP4467899B2 (en) | 2003-02-24 | 2010-05-26 | 株式会社デンソー | Refrigeration cycle equipment |
JP4411870B2 (en) * | 2003-06-13 | 2010-02-10 | ダイキン工業株式会社 | Refrigeration equipment |
CN1609518A (en) | 2003-10-21 | 2005-04-27 | 孙霆 | Air thermal energy heat pump type water heating stove |
US7040108B1 (en) | 2003-12-16 | 2006-05-09 | Flammang Kevin E | Ambient thermal energy recovery system |
US7178353B2 (en) | 2004-02-19 | 2007-02-20 | Advanced Thermal Sciences Corp. | Thermal control system and method |
US7721560B2 (en) | 2004-07-20 | 2010-05-25 | Carpenter Frank K | Climate control and dehumidification system and method |
WO2006039580A1 (en) | 2004-09-30 | 2006-04-13 | Carrier Corporation | Refrigeration system and method with controllable heat recovery |
US7237394B2 (en) | 2004-09-30 | 2007-07-03 | Carrier Corporation | Charge management for 100% heat recovery units |
JP3929067B2 (en) | 2004-12-09 | 2007-06-13 | 松下電器産業株式会社 | heat pump |
US20060213210A1 (en) * | 2005-03-24 | 2006-09-28 | Tomlinson John J | Low-cost heat pump water heater |
US20080197206A1 (en) | 2005-06-03 | 2008-08-21 | Carrier Corporation | Refrigerant System With Water Heating |
CN100549572C (en) | 2005-06-03 | 2009-10-14 | 开利公司 | Has the refrigerant charge control in the heat pump of water heating |
US7334419B2 (en) * | 2005-08-17 | 2008-02-26 | Bradford White Corporation | Heat pump water heater |
MX2008015586A (en) | 2006-06-07 | 2009-02-11 | Waters Hot Inc | Bio-renewable thermal energy heating and cooling system and method. |
US20070295018A1 (en) * | 2006-06-27 | 2007-12-27 | Williams Clifford C | Controlled flow heat extraction and recovery apparatus, method and system |
CN200972229Y (en) * | 2006-10-11 | 2007-11-07 | 钟志良 | Two-purpose machine of air-conditioning and water heating |
CN101169290B (en) * | 2006-10-27 | 2010-12-01 | 海尔集团公司 | Air conditioner device possessing water heater function |
KR100803144B1 (en) | 2007-03-28 | 2008-02-14 | 엘지전자 주식회사 | Air conditioner |
US8245949B2 (en) | 2007-07-25 | 2012-08-21 | Grand Hotel, LLC | Energy conservation system for using heat from air conditioning units to heat water supply lines |
DE102007039662B4 (en) * | 2007-08-22 | 2014-12-04 | Rheinmetall Waffe Munition Gmbh | charge igniter |
ATE507439T1 (en) | 2008-03-20 | 2011-05-15 | Daikin Ind Ltd | SPACE HEATING AND METHOD FOR CONTROLLING SPACE HEATING |
US20100000709A1 (en) | 2008-07-02 | 2010-01-07 | Tsung-Che Chang | Heating and heat recovery unit for an air conditioning system |
US8356481B2 (en) | 2008-08-07 | 2013-01-22 | Krassimire Mihaylov Penev | Dual hybrid fluid heating apparatus and methods of assembly and operation |
US8037931B2 (en) | 2008-08-07 | 2011-10-18 | Krassimire Mihaylov Penev | Hybrid water heating system |
US20100083950A1 (en) * | 2008-09-25 | 2010-04-08 | Bloxam Michael J | Solar energy water heating system |
US8422870B2 (en) * | 2009-02-13 | 2013-04-16 | General Electric Company | Residential heat pump water heater |
WO2010117973A2 (en) * | 2009-04-09 | 2010-10-14 | Carrier Corporation | Refrigerant vapor compression system with hot gas bypass |
CN102428327B (en) * | 2009-05-08 | 2014-12-10 | 山石科技有限公司 | Unit combined by water storage container and heat driven absorption heat pump |
CN101614451A (en) * | 2009-06-23 | 2009-12-30 | 王言明 | Heat pump type air conditioning system and heat recovery system |
JP5474483B2 (en) | 2009-10-16 | 2014-04-16 | 株式会社日立製作所 | Intermediate heat exchanger and air-conditioning hot water supply system using the same |
JP2011094931A (en) | 2009-10-30 | 2011-05-12 | Daikin Industries Ltd | Air-conditioning hot water supply system |
KR101639814B1 (en) | 2009-11-20 | 2016-07-22 | 엘지전자 주식회사 | Refrigerating and freezing combine air conditioning system |
US9618236B2 (en) | 2009-12-28 | 2017-04-11 | Daikin Industries, Ltd. | Heat pump system |
KR101192346B1 (en) | 2010-04-22 | 2012-10-18 | 엘지전자 주식회사 | Heat pump type speed heating apparatus |
KR20120002224A (en) * | 2010-06-30 | 2012-01-05 | 주식회사 보성테크 | Cooling and heating system for vehicle |
KR101758179B1 (en) * | 2010-07-23 | 2017-07-14 | 엘지전자 주식회사 | Heat pump type speed heating apparatus |
CN202018158U (en) | 2010-09-30 | 2011-10-26 | 邓锡伟 | Air-conditioning water heater |
CN102444986B (en) * | 2010-09-30 | 2014-04-16 | 艾欧史密斯(中国)热水器有限公司 | Duel-energy-source hot water supply system for implementing economical operation and operation method thereof |
KR101212698B1 (en) | 2010-11-01 | 2013-03-13 | 엘지전자 주식회사 | Heat pump type speed heating apparatus |
ES2663725T3 (en) * | 2011-01-27 | 2018-04-16 | Mitsubishi Electric Corporation | Heat pump apparatus and control method for heat pump apparatus |
US8438864B2 (en) * | 2011-03-04 | 2013-05-14 | General Electric Company | Transcritical heat pump water heater and method of operation |
KR20120136854A (en) | 2011-06-10 | 2012-12-20 | 삼성전자주식회사 | Water supply apparatus |
KR101507454B1 (en) | 2011-06-23 | 2015-03-31 | 삼성전자 주식회사 | Heat pump and method for controlling the same |
JP5775596B2 (en) | 2011-10-28 | 2015-09-09 | 株式会社日立製作所 | Hot water supply air conditioner |
US20130104574A1 (en) | 2011-11-02 | 2013-05-02 | Daniel J. Dempsey | Hybrid Space And Hot Water Heating Heat Pump |
US9389000B2 (en) | 2013-03-13 | 2016-07-12 | Rheem Manufacturing Company | Apparatus and methods for pre-heating water with air conditioning unit or heat pump |
CN204154044U (en) * | 2014-09-09 | 2015-02-11 | 广东欧科空调制冷有限公司 | The air-conditioning system of hot-gas bypass |
-
2014
- 2014-02-25 US US14/189,192 patent/US9389000B2/en active Active
- 2014-02-26 CA CA2905278A patent/CA2905278C/en active Active
- 2014-02-26 MX MX2015012306A patent/MX2015012306A/en unknown
- 2014-02-26 DK DK14779783.1T patent/DK2972008T3/en active
- 2014-02-26 WO PCT/US2014/018699 patent/WO2014163898A1/en active Application Filing
- 2014-02-26 CN CN201480013870.0A patent/CN105264305A/en active Pending
- 2014-02-26 EP EP14779783.1A patent/EP2972008B1/en active Active
- 2014-02-26 BR BR112015022343-5A patent/BR112015022343B1/en active IP Right Grant
- 2014-02-26 AU AU2014249864A patent/AU2014249864B2/en active Active
- 2014-03-13 CA CA3020438A patent/CA3020438C/en active Active
- 2014-03-13 CN CN201711159085.8A patent/CN108088114B/en active Active
- 2014-03-13 AU AU2014243719A patent/AU2014243719B2/en active Active
- 2014-03-13 EP EP14773958.5A patent/EP2972010A4/en not_active Withdrawn
- 2014-03-13 MX MX2015012402A patent/MX2015012402A/en active IP Right Grant
- 2014-03-13 EP EP19177498.3A patent/EP3591314A1/en active Pending
- 2014-03-13 CA CA2906662A patent/CA2906662C/en active Active
- 2014-03-13 CN CN201480024058.8A patent/CN105518397B/en active Active
- 2014-03-13 WO PCT/US2014/026894 patent/WO2014160514A2/en active Application Filing
- 2014-03-13 US US14/210,383 patent/US9879881B2/en active Active
-
2015
- 2015-09-10 CL CL2015002578A patent/CL2015002578A1/en unknown
-
2016
- 2016-07-11 US US15/207,170 patent/US9945582B2/en active Active
-
2017
- 2017-01-04 AU AU2017200042A patent/AU2017200042B2/en active Active
- 2017-11-06 AU AU2017258806A patent/AU2017258806B2/en active Active
-
2018
- 2018-01-29 US US15/882,756 patent/US10871307B2/en active Active
-
2020
- 2020-12-21 US US17/128,393 patent/US20210108829A1/en active Pending
Patent Citations (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4449375A (en) * | 1982-03-29 | 1984-05-22 | Carrier Corporation | Method and apparatus for controlling the operation of an indoor fan associated with an air conditioning unit |
US5628200A (en) * | 1995-01-12 | 1997-05-13 | Wallace Heating & Air Conditioning, Inc. | Heat pump system with selective space cooling |
US6357245B1 (en) * | 2001-05-01 | 2002-03-19 | Cohand Technology Co., Ltd. | Apparatus for making hot-water by air conditioner/heater |
US20050109490A1 (en) * | 2001-12-12 | 2005-05-26 | Steve Harmon | Energy efficient heat pump systems for water heating and airconditioning |
US20040144528A1 (en) * | 2002-02-12 | 2004-07-29 | Keijiro Kunimoto | Heat pump water heater |
US20060042285A1 (en) * | 2004-09-01 | 2006-03-02 | Behr Gmbh & Co. Kg | Stationary vehicle air conditioning system |
US20060179874A1 (en) * | 2005-02-17 | 2006-08-17 | Eric Barger | Refrigerant based heat exchange system |
US20090049857A1 (en) * | 2006-04-20 | 2009-02-26 | Carrier Corporation | Heat pump system having auxiliary water heating and heat exchanger bypass |
US20080245087A1 (en) * | 2007-04-07 | 2008-10-09 | John Walter Orcutt | System for controlled fluid heating using air conditioning waste heat |
US20090248212A1 (en) * | 2008-03-25 | 2009-10-01 | Cowans Kenneth W | Thermal control system and method |
US20140230477A1 (en) * | 2011-09-30 | 2014-08-21 | Daikin Industries, Ltd. | Hot water supply air conditioning system |
Cited By (50)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9945582B2 (en) | 2013-03-13 | 2018-04-17 | Rheem Manufacturing Company | Apparatus and methods for pre-heating water with air conditioning unit or heat pump |
US10871307B2 (en) | 2013-03-13 | 2020-12-22 | Rheem Manufacturing Company | Apparatus and methods for heating water with refrigerant from air conditioning system |
US9879881B2 (en) | 2013-03-13 | 2018-01-30 | Rheem Manufacturing Company | Apparatus and methods for heating water with refrigerant from air conditioning system |
US9353969B2 (en) * | 2013-06-26 | 2016-05-31 | Gd Midea Heating & Ventilating Equipment Co., Ltd. | Water tank and heat pump water heater comprising the same |
US20150000324A1 (en) * | 2013-06-26 | 2015-01-01 | Gd Midea Heating & Ventilating Equipment Co., Ltd. | Water tank and heat pump water heater comprising the same |
US20150338108A1 (en) * | 2013-07-26 | 2015-11-26 | Eco Factory Co., Ltd. | Air conditioning system and operation method for air conditioning system |
WO2016036688A1 (en) * | 2014-09-02 | 2016-03-10 | Rheem Manufacturing Company | Apparatus and method for hybrid water heating and air cooling and control thereof |
US10041702B2 (en) | 2014-09-02 | 2018-08-07 | Rheem Manufacturing Company | Apparatus and method for hybrid water heating and air cooling and control thereof |
US9945587B2 (en) | 2014-09-02 | 2018-04-17 | Rheem Manufacturing Company | Apparatus and method for hybrid water heating and air cooling and control thereof |
US10753661B2 (en) | 2014-09-26 | 2020-08-25 | Waterfurnace International, Inc. | Air conditioning system with vapor injection compressor |
US11480372B2 (en) | 2014-09-26 | 2022-10-25 | Waterfurnace International Inc. | Air conditioning system with vapor injection compressor |
US11927377B2 (en) | 2014-09-26 | 2024-03-12 | Waterfurnace International, Inc. | Air conditioning system with vapor injection compressor |
WO2016094949A1 (en) * | 2014-12-17 | 2016-06-23 | HABCHI, Jason | A hide-away air-conditioning system |
US10345004B1 (en) | 2015-09-01 | 2019-07-09 | Climate Master, Inc. | Integrated heat pump and water heating circuit |
US11067296B2 (en) * | 2015-11-20 | 2021-07-20 | Sens Geoenergy Storage Ab | Heat pump system and method for controlling a heat pump system |
US11690145B2 (en) * | 2015-12-17 | 2023-06-27 | Convotherm-Elektrogerate Gmbh | Method for operating a commercial cooking device and such a cooking device |
US20170211820A1 (en) * | 2016-01-26 | 2017-07-27 | Lennox Industries Inc. | Heating furnace using energy saving mode |
US9964313B2 (en) * | 2016-01-26 | 2018-05-08 | Lennox Industries Inc. | Heating furnace using energy saving mode |
US9945567B2 (en) * | 2016-01-26 | 2018-04-17 | Lennox Industries Inc. | Heating furnace using anti-stratification mode |
US20170211824A1 (en) * | 2016-01-26 | 2017-07-27 | Lennox Industries Inc. | Heating furnace using anti-stratification mode |
US20180347868A1 (en) * | 2016-02-08 | 2018-12-06 | Mitsubishi Electric Corporation | Air-conditioning apparatus |
US10684043B2 (en) * | 2016-02-08 | 2020-06-16 | Mitsubishi Electric Corporation | Air-conditioning apparatus |
US10235724B2 (en) * | 2016-06-01 | 2019-03-19 | International Business Machines Corporation | Energy efficient hot water distribution |
US20170351277A1 (en) * | 2016-06-01 | 2017-12-07 | International Business Machines Corporation | Energy efficient hot water distribution |
US10458678B2 (en) * | 2016-07-06 | 2019-10-29 | Rheem Manufacturing Company | Apparatus and methods for heating water with refrigerant and phase change material |
US20180010822A1 (en) * | 2016-07-06 | 2018-01-11 | Rheem Manufacturing Company | Apparatus and methods for heating water with refrigerant and phase change material |
US10871314B2 (en) * | 2016-07-08 | 2020-12-22 | Climate Master, Inc. | Heat pump and water heater |
US11448430B2 (en) | 2016-07-08 | 2022-09-20 | Climate Master, Inc. | Heat pump and water heater |
US20180010829A1 (en) * | 2016-07-08 | 2018-01-11 | Climate Master, Inc. | Heat pump and water heater |
US10794620B2 (en) * | 2016-09-12 | 2020-10-06 | Mitsubishi Electric Corporation | Air-conditioning apparatus |
US10866002B2 (en) | 2016-11-09 | 2020-12-15 | Climate Master, Inc. | Hybrid heat pump with improved dehumidification |
US11435095B2 (en) | 2016-11-09 | 2022-09-06 | Climate Master, Inc. | Hybrid heat pump with improved dehumidification |
US11143420B2 (en) * | 2016-12-21 | 2021-10-12 | Mitsubishi Electric Corporation | Air-conditioning apparatus |
US11859868B2 (en) * | 2017-10-30 | 2024-01-02 | Rheem Manufacturing Company | Hybrid water heater |
US11293666B2 (en) * | 2017-11-07 | 2022-04-05 | Nanjing University Of Aeronautics And Astronautics | Superhigh temperature heat pump system and method capable of preparing boiling water not lower than 100° C |
US10935260B2 (en) | 2017-12-12 | 2021-03-02 | Climate Master, Inc. | Heat pump with dehumidification |
US11719453B2 (en) | 2018-01-21 | 2023-08-08 | Daikin Industries, Ltd. | System and method for heating and cooling |
US11067319B2 (en) | 2018-03-05 | 2021-07-20 | Johnson Controls Technology Company | Heat exchanger with multiple conduits and valve control system |
US11953239B2 (en) | 2018-08-29 | 2024-04-09 | Waterfurnace International, Inc. | Integrated demand water heating using a capacity modulated heat pump with desuperheater |
US11592215B2 (en) | 2018-08-29 | 2023-02-28 | Waterfurnace International, Inc. | Integrated demand water heating using a capacity modulated heat pump with desuperheater |
US11215388B2 (en) * | 2019-01-21 | 2022-01-04 | Carrier Corporation | Refrigerant charge management |
US11506430B2 (en) | 2019-07-15 | 2022-11-22 | Climate Master, Inc. | Air conditioning system with capacity control and controlled hot water generation |
CN113137676A (en) * | 2020-01-20 | 2021-07-20 | 兄弟工业株式会社 | Air conditioner |
US11739952B2 (en) * | 2020-07-13 | 2023-08-29 | Rheem Manufacturing Company | Integrated space conditioning and water heating/cooling systems and methods thereto |
US20220010978A1 (en) * | 2020-07-13 | 2022-01-13 | Rheem Manufacturing Company | Integrated space conditioning and water heating/cooling systems and methods thereto |
US11781760B2 (en) | 2020-09-23 | 2023-10-10 | Rheem Manufacturing Company | Integrated space conditioning and water heating systems and methods thereto |
US11747058B2 (en) | 2020-11-10 | 2023-09-05 | Rheem Manufacturing Company | Air recirculation systems for heat pumps |
WO2022103726A1 (en) * | 2020-11-10 | 2022-05-19 | Rheem Manufacturing Company | Air recirculation systems for heat pumps |
US11754316B2 (en) * | 2021-04-26 | 2023-09-12 | Villara Corporation | Providing domestic hot water from conventional residential split system heat pumps |
US20220341628A1 (en) * | 2021-04-26 | 2022-10-27 | Villara Corporation | Providing domestic hot water from conventional residential split system heat pumps |
Also Published As
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US20210108829A1 (en) | Apparatus and methods for heating water with refrigerant from air conditioning system | |
AU2017293847B2 (en) | Apparatus and methods for heating water with refrigerant and phase change material | |
CN107003010B (en) | Apparatus and method for hybrid water heating and air cooling and control thereof | |
US11953239B2 (en) | Integrated demand water heating using a capacity modulated heat pump with desuperheater | |
US10156396B2 (en) | System for operating an HVAC system having tandem compressors | |
KR101611315B1 (en) | Air conditioner and operating method thereof | |
US11543142B1 (en) | Systems and methods for operation of a climate control system | |
EP2622523B1 (en) | Hot water prioritization |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: RHEEM MANUFACTURING COMPANY, GEORGIA Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:HAWKINS, TIMOTHY B.;BABB, JEREMY L.;REEL/FRAME:033491/0239 Effective date: 20140611 |
|
STCF | Information on status: patent grant |
Free format text: PATENTED CASE |
|
MAFP | Maintenance fee payment |
Free format text: PAYMENT OF MAINTENANCE FEE, 4TH YEAR, LARGE ENTITY (ORIGINAL EVENT CODE: M1551); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY Year of fee payment: 4 |